DE102018007650B4 - Intermittent combustion engine - Google Patents

Abstract

The invention relates to an internal combustion engine with intermittent combustion of a fuel-gas-air mixture (diagram), with a housing ring (2) which forms the eccentric housing (31) with the diameter 2 × R with two side parts (13g) and (13öl). The rotatable eccentric shaft (7), which has an eccentric extension with eccentricity e, is centrally mounted in this space Eccentric ring (1) with the outer diameter = (2 × R) - (2 × e) are formed in the larger housing ring (2). All the mass points of the eccentric ring (1) move due to its eccentric bearing on the eccentric shaft (7) and the additionally leading slide valves (4) in the eccentric chamber space (3a) on the circular path with the diameter 2 xe, the eccentric ring (1) is held securely on its circular path by evenly radially arranged, in both rings (1) and. (2) pivotable and radially displaceably mounted in a large number of separating slides (4), which divide the eccentric chamber (3a) into small working chambers (3) with their combustion chambers (8). The separating slides (4) with the domes (5) seal the working chambers (3) from each other. The working chambers (3) lead with the fuel gas pressure from the combustion chambers (8) to the rotation of the eccentric shaft (7) due to the eccentricity e Gas housing (16) drives the eccentric shaft (7) via planetary gear sets (15) to the gas exchange ring (9) with the aid of the control loop for gas supply and discharge or sealing of the combustion chambers (8). The eccentric ring (1) closes at top dead center the respective combustion chamber (8) with extremely high turbulence, which is responsible for the homogeneity of the fuel-air mixtures Combustion conditions are maintained. An exemplary embodiment with a 0.9 L working space clearly explains the scope of the invention with its possibilities for various combustion strategies posed.

Description

State of the art

The present invention is driven by the idea that only a work on the “effective combustion chamber” can lead to a remarkable improvement of the internal combustion engine system with intermittent combustion.

• Um einen „effektiven Brennraum“ zu schaffen hat schon Harry Ricardo vor 100 Jahren versucht, Brennraum vom Hubraum abzugrenzen. Es ist ihm aus verschiedenen Gründen nicht vollkommen gelungen. Hier sollen nur zwei Ursachen für das suboptimale Ergebnis von Ricardos Brennraum herausgestellt werden: (s. Nichtpatentliteratur)

Since only extensive consideration of the more than 100 years of intensive development in this area can be successful, this, representative of my approach, is summarized with an interesting example:

• In order to create an "effective combustion chamber", Harry Ricardo tried 100 years ago to separate the combustion chamber from the displacement. For a number of reasons, he did not succeed. Only two causes for the suboptimal result of Ricardo's combustion chamber should be highlighted here: (see non-patent literature)

The desired turbulence in the compression cycle for homogenization was so great that, with the high flame speed achieved with it, a large proportion of the mixture in the wide and fast-opening displacement led to knocking (detonation).

This process, which leads to the “rough” run, was reinforced by the hot exhaust valve in the combustion chamber.

• Für die vorliegende Erfindung sind aber zur Gesamterfassung des akuten Standes auch Kurbeltrieb, Hochleistungswerkstoffe, Schmierungstechnik, Kraftstoffentwicklungen und Verfahrensstrategien zu betrachten:

The result was that Ricardo had to reduce the efficient higher compression before the later development of fuels with a higher octane number started and newer, more intensive ignition systems were available, such as multi-channel flame ignition, known as "jet ignition", which is evidently caused by a kind of flame jet leads to flame speeds (> 20 m / s) which cause the entire combustion chamber to react in a very short time (<1 ms) before incompletely burning residual mixture can even occur in the edge area. The range from Ricardo to the "jet ignition" is demanding, but shows how crucial the development of the combustion conditions is for the present invention:

• For the present invention, however, crank drive, high-performance materials, lubrication technology, fuel developments and process strategies are also to be considered for the overall detection of the acute state:

Combustion chamber and gas exchange technology

The combustion chamber development to the current state is characterized by the advances in charge control through the introduction of variable valve control for influencing the combustion gas flows, through adapted forms of the cylinder head and piston side and through the intensive development of injection technology.

The flows of the fuel gases are used more and more intensively for the homogenization of the fuel-EGR-air mixtures even during the intake stroke in the 4-stroke process. The valve stroke adjustment e.g. of the Valvetronic system integrated in the engine management brings about a swirl with a small valve lift while throttling the intake air, which shows a noticeable improvement in the fuel-air EGR mixture. With the internal EGR components, which can be influenced by adjusting the valve timing, and especially with external EGR components, partly cooled and also added to the fresh air flow before the turbochargers, combustion temperatures and above all, for self-igniters, ignition delays are influenced to determine the process.

The progress is particularly evident through the use of variable valve control in multi-valve engines, where the different stroke widths and times of side-by-side intake valves are used for partial shutdown. In addition to optimizing the valve timing, the use of different combustion chamber shapes determines the degree of gas homogenization, insofar as the size and position of the valve disc permit. (see non-patent literature: Hack, Indra: multi-valve, FIAT-Schäffler: electro-hydraulic valve train) In particular, the gasoline petrol engine was followed by the so-called "Hemi" shape of the combustion chamber design to achieve the triple goal: exhaust gas quality To achieve efficiency and performance. The use of the roof shape in the cylinder head, to name just one example, has the effect of approximating a combustion chamber that is as compact as possible, above all because of the favorable V position of the valves, especially with the multi-valve. widespread and a good perfection found. The complex V-arrangement of the valves favored the introduction of double camshaft engines, which in turn are a favorable starting point for fully variable valve control. The compactness of the combustion chamber in TDC was improved by roof-shaped piston surfaces and the pinch surfaces from the piston edges were optimized for better swirling, as far as the valve discs protruding from the overlap area allow. The resulting fuel gas flows, which take the form of a roller in the roof-shaped combustion chamber, act at the ignition time shortly before ZOT and improve homogeneity and increase the burning rate. (see non-patent literature)

The squeezing currents are called squish and are very much considered in the development. (see non-patent literature, ISAE Symposion Proceedings 1998)

The alternatives to the poppet valves as gas exchange components such as roller turn, flat and rotary slide controls in the cylinder head and also in the cylinder block area of reciprocating engines have so far not been pursued due to their low durability and poor sealing properties. The disadvantages of the slide-controlled 2-stroke and Wankel engines have led to developments with poppet valve-controlled 2-stroke engines, especially in large engine construction with external compression.

The poppet valve control is also used for smaller engines, such as the Z engine from Finland. (see non-patent literature)

Patented proposals from the 1970s, such as those mentioned in the DD 59 645 A1 Proposed internal combustion engine with rotating eccentric rings, combustion chamber-forming pendulum slide valves and transfer channels for 2-cycle gas changes should avoid the disadvantages of the Wankel circle piston engines, such as wear, lubrication and high fuel consumption. These suggestions did not lead to series production, since the development possibilities presented, such as simple geometry, inexpensive materials, smooth running, low sliding speeds and a variety of processes, were not pursued with determination due to the concentration on the 2-stroke process. The present invention also takes up these development possibilities, in particular by designing the combustion chamber, the choice of materials and the variety of processes to achieve the decisive factor for optimum efficiency, effort and minimal pollution.

Not only the use of suitable materials and coatings, but also the use of highly dynamic control systems to take into account the extremely diverse load requirements play a decisive role here.

The other extreme main shape besides the Hemi shape is the so-called “Heron” design of the combustion chamber, whereby the combustion chamber lies as a round trough in the piston surface with a flat cylinder head.

The Heron combustion chamber, which is often designed as a ring-shaped depression for diesel operation, favors the gas flows with a relatively wide squish ring around the central combustion chamber bowl during the compression cycle even while fuel is being injected. A particularly effective flat squish surface has been realized without overlapping valve times.

The use of direct injection also in Otto engines and their further development to very precise and dynamically metering multi-drop injection valves with eight and more single jet pulses, which are used in multiple nozzles with adapted outlet angles, has become common practice. Here, the system called "Common Rail" plays a dominant role due to its advantages such as stable input pressure of the fuel and fine metering through electronic pulse drive using piezo crystals. Fine metering with fuel rates <5 mm ³ per 4-stroke cycle / combustion chamber are common practice.

With these properties, diesel and petrol applications are carried out with several pre-injections and subsequent main injection for more effective use of the very short-term (<2 ms) mixing and evaporation time frame of the fuel. The application is very suitable for future success with homogeneous preparation of the fuel mixtures in gasoline and HCCI operation.

Crank drive, lubrication, cooling

Crankshafts and conrods guided in plain bearings have become a matter of course in everyday use with very proven precision and good service life. Intensive tests, manufacturing accuracy, safe Lubrication conditions including temperature-controlled oil coolers, pressure-controlled pumps, fine filters and advanced, application-oriented oil qualities help to ensure longevity.

Oil pumps with working pressures <6 bar are sufficient for the supply of pressurized oil to the plain bearings through hollow-drilled crankshafts.

Gear pumps are being replaced by self-regulating impeller and swivel gear pumps. The nine plain bearings oil-fed in the 4-cylinder petrol or diesel engine release their oil into the crankcase well swirled and also lubricate and cool the piston and cylinder surfaces. For pistons with higher loads, oil spray nozzles are used to cool the piston crown. The central oil pump also achieves the cooling effect of the extensive camshaft bearings and adjustment devices of the cylinder heads that is used in addition to water cooling. The water cooling of the exhaust gas areas in the cylinder heads is also increasingly used for quick heating of the cooling water during a cold start. Dry sump lubrication systems are used in series in dynamically heavy-duty sports cars and SUVs.

Rolling bearings for the main and connecting rod bearings are not used for large series engines because of the very complex composite crankshafts required.

The development of ball and roller bearings to high-precision, heavy-duty and long-lasting machine elements is significantly promoted by the influence of IT-controlled manufacturing technology.

Various engine manufacturers have been working on developments for a long time that want to design variable compression ratios and / or stroke volumes or alternate movements of the piston movement with crankshaft adjustments. Infinitely variable, hydraulically operated conrod lengths or the positional variation of the crankshaft axis are in an advanced stage of development.

Here, the variation of the compression ratio during operation with a potential of about 10% is seen as the most interesting way of improving the efficiency of highly developed, supercharged gasoline engines, but has not yet been used in large series.

The adjustment of the crankshaft axis perpendicular to the piston axis investigated to improve the torque development is also at an advanced stage of development.

Materials

Light metal materials (aluminum and magnesium alloys) for crankcases, cylinder heads, pistons, oil and water pumps and oil sumps have been in series production with wear-resistant alloys for cars for decades. For heavily loaded cylinder liners in aluminum cylinder blocks, liners made of cast iron materials or high-alloy aluminum alloys are used for the cylinder block for reasons of weight and, for cylinder heads, also for high heat dissipation.

The use of cast iron materials for the workpieces mentioned has proven itself for various applications, such as diesel engines, particularly because of the sometimes superior durability. The application is promoted by continuous improvements in the casting of filigree components and above all by improvements in material properties such as ductility and wear resistance. The cast iron material GJV with high tensile strength and very good wear properties is used for cylinder crankcases with an advantageous piston track. The application is also promoted for smaller diesel engines by solving weight problems due to the advanced casting technology.

Lubricants

Various research institutes are investigating dry lubricants that are permanently stored in the porous surface of the workpieces subject to friction.

Fuels

The most interesting development in the field of fuels for diesel and gasoline engines is the work on oximeethylene ether OME. This fuel, which is also obtained from renewable resources Due to its molecular content of oxygen, it has the property of forming CO ² very thoroughly and thus burning soot-free and also NOx-free. (see non-patent literature: TUM combustion machines, 2016, et al.)

Combustion strategies

The current development of a new combustion engine from Mazda is planned in a car for start in 2019.

This engine is operated according to the strategy of the Homogeneous Charge Compression Ignition "HCCl". At Mazda, this operating mode is supported by spark ignition with spark plugs, in order to drive in load areas that do not reach auto-ignition safely and controllably. (Non-patent literature: Mazda, company reports and Timo Janhunen Aumet Oy: HCCI-Combustion in the Z Engine)

Conclusion

The subject matter for the present invention is improvement of the homogeneity of combustion mixtures, use of small combustion chambers and squishing turbulence, compliance with optimal, punctiform combustion parameters, possibly by selecting ignition sequences. Technological requirements such as high-quality materials and coatings as well as advanced fuel injection technology are available.

Non-patent literature

• Harry Ricardo, 1885-1974, Wikipedia,
• Multi-valve engines, G. Hack, F. Indra, ISBN 978-3-613-02260-7
• Squish design, e.g. Takanori Ueda et.al. "Effects of Squish Area Shape on Knocking", ISAE symposion proceedings, Vol. 982 p. 99.1998. --- Engine combustion process, kfztech.de INGENIEUR.de, 2010/03, FIAT-Schäffter, electronic-hydraulic valve train,
• SkyActiv-X petrol engine, gasoline self-igniter at Mazda, press review 03/2017, "Experimental and numerical investigation of the autoignition mechanisms for HCCl gasoline operation", Sauter, Werner et. al. University of Karlsruhe, Institute for Piston Machines ,
• TUM, combustion machines, 02/12/2016: "Fuels that do not produce harmful exhaust gases", Dr. Härtl, Martin; TUD, ---- Münz, Markus, "OME development"
• The Z-Engine: Internal Combustion Engine Laboratory at the Helsinki University of Technology (HUT) and the Energy Technology Department at the Lappeenranta University of Technology (LUT).
• HCCI-Combustion in the Z Engine, Author: Timo Janhunen Aumet Oy, Leankuja 4, 07230, Finland,

Task

The present invention on internal combustion engines with intermittent combustion is intended to make the limits of the current stages of development permeable.

As the history of development shows, the design of the combustion chambers plays a restrictive role in the piston engines, depending on the expansion space or working space displacement. In many cases, therefore, interesting possibilities, such as safe auto-ignition operation when burning exhaust-gas-neutral fuels, can only be used under restrictive conditions. As a result, no further developments are encouraged.

Thus, the present invention focuses on the design of combustion chambers and their working environment, such as gas exchange, sealing, lubrication, cooling, control elements and combustion strategies. The possibilities according to the invention are intended to promote both the necessary intensive homogeneity of the fuel gases and the concentration of the main combustion reaction on the combustion chamber.

In this effective combustion chamber, which due to its small size and compact shape must be characterized by short burning times, the operating values such as fuel rate, air ratio λ, EGR rate, speed, charge change, boost pressure, compression ratio, wall temperatures and homogeneity of the ignitable fuel / air Develop mixtures to the required safe and optimal operating point with regard to consumption and pollutant content.

The object of the invention is thus expanded in that this optimum operating point is to be maintained under all load requirements of the intended use.

Solutions of the invention and embodiment

1. 1. Geometric-mechanical basics
2. 2. Solutions for the sealing systems
3. 3. Lubrication, cooling
4. 4. Combustion process strategies

Geometric-mechanical basics

The invention relates to an internal combustion engine according to the preamble of claim 1 with intermittent combustion of the fuel-air mixture, which e.g. emits its thermo-mechanical energy according to the well-known 4-stroke process in a multi-chamber system, externally or compression-ignited.

Eccentric-operated work chambers ( 3rd ), whose gas exchange from gas exchange rings supported by the control loop ( 9 ) is carried out.

• Der Aufbau der Maschine fundiert auf dem Gehäusering (2), der mit den Seitenteilen (13g) und (13öl) das Exzentergehäuse (31) bildet.

The essential components of the invention are shown on the basis of the schematic sketch on the enclosed diagram. (Fig. Scheme):

• The structure of the machine is based on the housing ring ( 2nd ) with the side parts ( 13g ) and ( 13 oil ) the eccentric housing ( 31 ) forms.

In the eccentric housing ( 31 ) is the rotatable eccentric shaft ( 7 ), which has an extension with the eccentricity e, mounted centrally.

In this eccentric housing ( 31 ) the smaller, circular eccentric ring circulates ( 1 ), the circular inner surface of the housing ring ( 2nd ) following at the smallest distance by standing on the eccentric extension of the eccentric shaft ( 7 ) is stored.

Depending on the task, the large number of smaller combustion chambers ( 8th ) with limited installation space with a circular arrangement in the side part ( 13g ) brought in.

The associated working chambers ( 3rd ) by evenly dividing the crescent-shaped space ( 3a ) around the in the housing ring ( 2nd ) circulating eccentric ring ( 1 ) by slide gate ( 4th ) formed, which are known as pendulum valves of internal combustion engines and oil pumps ( DD 59 645 A1 and DE 10 2010 024 222 A1 2011.10.13).

The separating slide ( 4th ) also take on the task of 1 ) to run on its circular path without self-rotation.

The one in the gas housing ( 16 ) centric, circular and rotatable gas exchange ring ( 9 ) from the eccentric shaft ( 7 ) is driven, with evenly arranged channels causes the gas exchange of all combustion chambers ( 8th ).

The sum of the individual gas forces of the working chambers ( 3rd ) drive onto the eccentric ring ( 1 ) acting, the eccentric shaft ( 7 ) with the lever = ex cos α. ( 5 )

In a partially schematic embodiment of the invention with about 0.9 liters of work space and 15 combustion chambers ( 8th ) are explained in more detail below: In 1 is in longitudinal and cross-section through the eccentric housing ( 31 ) the eccentric ring ( 1 ) inside the housing ring ( 2nd ) where it is connected by means of the 15 separating slides ( 4th ) the 15 working chambers ( 3rd ) generated.

The necessary change in volume of the working chambers ( 3rd ) is due to the circulation of the eccentric shaft ( 7 ) mounted circular eccentric ring ( 1 ) in a circular housing ring that is 2 × e larger in diameter ( 2nd ) (with + tolerance for minimum gaps in the warm operating state).

Ie, the circulation of the eccentric ring ( 1 ) is a movement of the center of gravity of (1), here the center of (1) for reasons of symmetry, and all of its mass points on a circular path with a diameter of 2 × e without self-rotation.

So that the eccentric ring ( 1 ) can carry out this circulation, it must be self-rotating through the isolating slide ( 4th ) can be prevented because it moves when the eccentric shaft ( 7 ) would be taken along by the resulting bearing friction. Due to the (with 4-stroke) odd number of 15 Slide valves ( 4th ) this task is carried out with little vibration. To do this, the separating slides are evenly distributed radially ( 4th ) in the eccentric ring ( 1 ) and in the housing ring ( 2nd ) around the angle δk ( 6 ) swiveling and sliding in domes ( 5 ) sealed sealed. ( 13 and 14 )

The working space of the internal combustion engine of the selected example is: Working space [cm ³ ] = (inner circumference of the housing ring ( 2nd ) - number of working chambers ( 3rd ) × slide gate thickness) × housing ring width × 2e = e.g. (16 × 2π - 15 × 0.6) × 8 × 1.2 = 879 cm ³

( 11 , 12th , 13 )
With the slide valves ( 4th ), according to the main claim or claim 2, both the sealing of the resulting working chambers ( 3rd ) as well as the low-vibration circulation of the eccentric ring ( 1 ) reached.

Through the decisive dimensioning of the contact angle δk ( 6 ) the isolating slide ( 4th ) in the dome slot ( 4e ) from eccentric ring ( 1 ) and housing ring ( 2nd ) the eccentric ring ( 1 ) so that all earth points of the eccentric ring ( 1 ) and its built-in parts describe circles with Ø = 2 × e.

{11) und (13)}The docking angle δk ( 6 ) corresponds to the max. Swivel angle δk from the 0 position in the exemplary embodiment at UT and is from e and the center distances k1 and k2 of the calottes ( 5 ) according to the formula $$\text{tan}\mathrm{\delta }=\text{sin}°\text{EW}/\left\{1+\left[\left(\text{<figure-callout id="1" label="k" filenames="DE102018007650B4\_0002.png,DE102018007650B4\_0003.png" state="{{state}}">k</figure-callout>}1+\text{k}\mathrm{2nd}\right)/\text{e}\right]-\text{cos}°\text{EW}\right\}\text{dependent}\text{.}$$

{ 11 ) and (13)}

The sum k1 + k2 is the smallest center-to-center distance of the calottes ( 5 ) as the eccentric ring approaches ( 1 ) in the position OT to the housing ring ( 2nd ) with the eccentric position ° EW = 12 °. ° EW is the position angle on the housing ring ( 2nd ) based on OT = 0 ° in the example, 1 .

• Wie der max. Schwenkwinkel= Anlegewinkel δk (6) des Ausführungsbeispiels mit e = 6 mm, k1 + k2 = 26 mm und die im Anlegebereich der Trennschieber bei 10,8 ° flach verlaufende Kurve über dem Exzenterwinkel °EW zeigt, werden z.B. mit der Brennraumzahl 15 sehr kleine Schwingungsweiten der Trennschieber (4) von < 0,1 mm innerhalb von zwei Anlegepositionen erreicht.

16 shows the course of the swivel angle δ ( 6 ) over the eccentric winding ° EW, where the positions of the separating slides ( 4th ) from the cross section of the 1 are highlighted by small circles:

• As the max. Swivel angle = contact angle δk ( 6 ) of the exemplary embodiment with e = 6 mm, k1 + k2 = 26 mm and the curve in the contact area of the separating slide at 10.8 ° which shows a flat curve above the eccentric angle ° EW are, for example, with the number of combustion chambers 15 very small vibration ranges of the separating slide ( 4th ) of <0.1 mm within two positioning positions.

In other words: within a 0.8 ° difference of the contact angle there are three separating slides that cover 48 ° EW.

The idea that the eccentrically mounted and from an eccentric shaft ( 7 ) circular eccentric ring ( 1 ) in the triangle of 2 adjacent slide valves, namely one positioned in the area 80 ° before and after TDC and the eccentric center as in a prism, describes very clearly the geometrically stable situation and the absorption of the tangential forces which are exerted in the direction of rotation by the eccentric shaft ( 7 ) as a frictional force on the eccentric ring ( 1 ) act.

The low-vibration circulation of the eccentric ring ( 1 ) is further improved by coordinating the width of the dome slots ( 4e ) in 13 with the radial moment of inertia of the slide valve ( 4th ). Small spring stiffness of the separating slide ( 4th ) facilitates the desired simultaneous overlap and low-stress creation of several slide gates ( 4th ), ( 16 ) in the dome slot ( 4e ). The consideration of the temperature-related expansions for the stable guidance of the eccentric ring ( 1 ) are facilitated by these votes.

The obvious analogy to absorbing the tangential forces, as in the known radial engine due to its main connecting rod, would result in an oscillating movement of the eccentric ring ( 1 ) and thus too an additional load on the eccentric shaft ( 7 ) to lead. This disturbance of a low-vibration, quiet run is caused by the symmetrical arrangement and even distribution of all separating slides ( 4th ) avoided. ( 1 )

During the operation of this eccentric rotary valve motor, the eccentric ring ( 1 ) Tangential force due to the gas forces in the working chambers ( 3rd ) and due to the friction in the bearing of the eccentric ring ( 1 ).

In order to minimize this torque, which loads the isolating slide guide, the use of roller bearings is recommended ( 29 ), ( 30th ), which is used for motors with only one eccentric ring ( 1 ) are very easy to install.

Another, very precise circulation guide of the eccentric ring ( 1 ) with multiple rolling receptacles in the holes ( 62 ) takes over the isolating slide load. ( 1 and 6 )

The leadership roles ( 62a ) take over the tangential forces of the bearing friction through at least 3 evenly distributed permanent circular contacts in the relief bores ( 62 ) either in the eccentric ring as shown here ( 1 ) or in the side parts ( 13 ).

The relief drilling ( 62 ) roll on the guide rollers ( 62a ) which, in the event of heavy use, in both side parts ( 13 ) are stored and the entire thickness of the eccentric ring ( 1 ) to wear. The relief drilling ( 62 ) roll with their center on a circle of diameter = 2 × e without play on the guide rollers ( 62a ).

The 6 shows the selected embodiment of the 0.9 L engine with bore ( 62 ) Ø 24 mm, which is on a guide roller ( 62a ) rolls with 012 mm and thus describes a center circle of 012 mm = 2 × e.

Since the isolating slide ( 4th ) in the housing ring ( 2nd ) are held radially and the pivotal movement of the opposite separating slide ( 4th ) in opposite directions, practically complete balancing of the eccentric ring system ( 1 ) Eccentric shaft ( 7 ) Isolating slide 84 ) by the counterweights of the eccentric shaft ( 7 ) can be made. With a large number of e.g. 15 Chamber spaces ( 3rd ) and thus 15 Slide valves ( 4th ) there is not only very good synchronism, but a load due to resonance between the eccentric ring ( 1 ) stimulating torsional vibration of the light separating slide ( 4th ) and the large moment of inertia of the eccentric ring ( 1 ) is avoided, better surface coverage in TDC between eccentric ring ( 1 ) and housing ring ( 2nd ) is achieved in the chamber area, which minimizes harmful chamber space and the separation between effective combustion chambers ( 8th ) and working chambers ( 3rd ) improved.

Details of the separating slide ( 4th ) are described in the section “Solutions for the sealing systems [0010] and the following.

A main reason for the development of internal combustion engines is the optimization of the combustion processes with intermittent combustion. Here, the design (size, shape, material) of the combustion chamber, which must take into account the arrangement of the gas exchange elements, ignition or glow system and possibly the injection device, plays a decisive role. Added to this is the inclusion of the working volumes of the individual combustion chambers, which often cannot be optimally designed due to space constraints, even though the burning lengths in the reaction space and thus the use of the available reaction time is decisive for the quality of the implementation.

Since the average process times of the individual cycles e.g. With the 4-stroke process in most applications in the order of magnitude of only <10 milliseconds (n = 3000rpm), reaction distances and speeds are crucial for the quality and precision of homogenization processes in the preparation of the air-fuel mixture to be burned also responsible for the results of the combustion with regard to completeness / efficiency and quality of the exhaust gases. Especially when liquid fuels are injected.

• - große Turbulenz mit asymmetrischem Squish (auch Squeezing genannt) während des Kompressionstakts mit einem Flächenverhältnis > 10 von der Kammerfläche in den Brennraumeinschnitt 10 hinein. (V_mittel > 20 m/s bei n = 3000U/min)
• - Abtrennung der Brennräume (8) von den Arbeitskammern (3) durch engen Spalt während der Brennzeit.

For the combustion chamber to be registered here ( 8th ) It is important that the effective combustion processes are already completed at 30 ° EW after TDC, ie after about 1.5 ms after TDC, so that we can speak of an effective combustion chamber here, as with a 0.9 L engine, for example 15 Combustion chambers and e = 6 mm the gap between the housing ring ( 2nd ) and the eccentric ring surface ( 1 ) at this time only about 0.8 mm has opened. The requirements for the effective combustion chamber ( 8th ) according to the invention by the circular arrangement of a large number of small combustion chambers ( 8th ) with working chambers ( 3rd ) as work spaces:

• - Great turbulence with asymmetrical squish (also called squeezing) during the compression stroke with an area ratio> 10 from the chamber surface into the incision in the combustion chamber 10th inside. (V _average > 20 m / s at n = 3000rpm)
• - separation of the combustion chambers ( 8th ) from the labor chambers ( 3rd ) due to narrow gap during the burning time.

• Der Brennraum (8) wird über einen Einschnitt (10) im Gehäusering (2) mit der Arbeitskammer (3) verbunden. Für ein starkes Kompressions-Squeezing mit 90% des Kammervolumens ist dieser Einschnitt (10) gegen die Exzenterbewegung geneigt. Der Einschnitt (10) trägt die Einspritz- und Zündeinrichtungen (11).

In 7 with the enlargements 8 u . 9 the details of the construction are clarified:

• The combustion chamber ( 8th ) is made using an incision ( 10th ) in the housing ring ( 2nd ) with the Chamber of Labor ( 3rd ) connected. For a strong compression squeezing with 90% of the chamber volume, this incision ( 10th ) inclined against the eccentric movement. The incision ( 10th ) carries the injection and ignition devices ( 11 ).

In addition, the incision ( 10th ) with a helical tension to increase the twist and / or incisions in the eccentric ring ( 1 ) are carried out.

The induced swirl function during the intake process is activated via the short intake duct (which is positioned at an angle to the combustion chamber opening ( 12th ) in a separate gas housing ( 16 ) arranged gas exchange ring ( 9 ) reinforced.

This effect of the intake swirl becomes the desired fuel + EGR + air homogenization in the maximum turbulent flow of the gas exchange, especially when using a turbocharger or an electric charger that is more economical in terms of performance, in conjunction with an up to 50 ° EW overlap of the gas exchange entire intake stroke.

The inlet swirl detects the internal I-EGR in the early phase of the inlet and prepares it, for example, when operating with split fuel injection P1 and P2 partial injection before the late intake stroke.

In the view of the gas exchange channels, inlet ( 12th ) and outlet ( 65 ), of the 9 is the intersection of outlet and inlet = 0 °, as is clearly shown in chamber number II.

The position of the gas exchange opening and closing can only be specified by driving over the combustion chamber openings, since this is where the gas flow begins and not when the channel openings enter the inner surface of the spiral band springs ( 14 ). These spring rings reduce the blowby and provide the preload for the application system of the gas exchange ring ( 9 ) representing the generation of the drive torque of the gas exchange ring ( 9 ) is responsible at the start of the engine and thus one of the most important feedbacks about the condition of the contact sliding surface for the application control loop of the gas exchange ring ( 9k ) is. Also for the required basic load of the axial ball bearing ( 21 ) ensures the preload ( 19a ) of the coil tape springs ( 14 ).

• - vermeidet aber durch Entfall der heißen Ventilköpfe die Klopfanfälligkeit,
• - in der gleichen Richtung wirken die sehr kurzen Brennstrecken (20...30 mm) der kleinvolumigen Kammereinheiten,
• - zusätzlich wird bei den sehr kurzen Brennzeiten durch hohe Brenngeschwindigkeit infolge Turbulenz nicht nur der Kraftstoff optimal ausgebrannt, sondern es werden auch zur Klopfneigung führende Randverdichtungen von Gasresten minimiert,
• - die große Querschnittsfläche des Einschnittes (10) zwischen effektivem Brennraum (8) und Arbeitsraum (3) sowie die geringe Radialgeschwindigkeit des Exzenterringes (1) (n=3000 → 0,7m/s) vermindern Strömungsverluste bei maximal 12 m/s bei n = 3000 U/min,
• - die ebene Brennraum-Verschlussfläche des Gaswechselringes (9) bietet keine überhitzten Kanten und dreht sich mit geringer Geschwindigkeit permanent weiter, wodurch die Berührung mit dem wassergekühlten Seitenteil (13g) und die gleichzeitige Durchströmung des Gaswechselringes (9) mit Einlassluft für Kühlung sorgen.

The described combustion chamber arrangement ( 8th ) outside the Chamber of Labor ( 3rd ), corresponds to the procedure used by Ricardo to separate the combustion and working space and fulfills the task according to the invention:

• - but avoids knocking by eliminating the hot valve heads,
• - The very short burning distances (20 ... 30 mm) of the small-volume chamber units work in the same direction,
• - in addition, with the very short burning times due to the high burning speed due to turbulence, not only is the fuel optimally burned out, but also edge compression of gas residues that leads to knocking is minimized,
• - the large cross-sectional area of the incision ( 10th ) between effective combustion chamber ( 8th ) and work space ( 3rd ) and the low radial speed of the eccentric ring ( 1 ) (n = 3000 → 0.7m / s) reduce flow losses at a maximum of 12 m / s at n = 3000 rpm,
• - the flat combustion chamber sealing surface of the gas exchange ring ( 9 ) does not offer any overheated edges and rotates continuously at low speed, making contact with the water-cooled side part ( 13g ) and the simultaneous flow through the gas exchange ring ( 9 ) provide cooling with intake air.

• - Effizienz verbessernd wirken auch die geringeren Wärmeverluste durch die in Vermicular-Guss (GJV) ausgeführten Seitenteile (13) und Exzenterring (1) aus Sphäroguss (GJS), die einen großen Teil des Brennraums (8) bilden,
• - die gemeinsame Gestaltung des Brennraums (8) mit der Beteiligung von Seitenteil (13g), Gehäusering (2) und auch durch Aussparungen im Exzenterring (1), wie in 10 mit der unterbrochenen Kontur angedeutet, verbessert die Form des Brennraums (8) und (10). Bei Ausführung der anspruchsvollen Verbrennungsstrategie „HCCl“ mit erweitertem Leistungsbereich wird mit Sphäroguss 50 (GJS) oder ähnlichen eisenbasierten Werkstoffen für den Gehäusering (2) der gesamte Arbeitsraum hinsichtlich Wärmeverluste und Dehnungsverhalten verbessert. (Hinweispunkt [0028])

With the hot exhaust gases that flow parallel to the intake air and the water-cooled gas housing ( 16 ) z. B. made of aluminum alloy, arises in the ring volume of the gas exchange ring ( 9 ) a lower average temperature of <300 ° C.

• - Efficiency is also improved by the lower heat losses due to the side parts made in vermicular cast iron (GJV) ( 13 ) and eccentric ring ( 1 ) made of ductile iron (GJS), which covers a large part of the combustion 8th ) form,
• - the joint design of the combustion chamber ( 8th ) with the participation of side part ( 13g ), Housing ring ( 2nd ) and also through recesses in the eccentric ring ( 1 ), as in 10th indicated by the broken contour, improves the shape of the combustion chamber ( 8th ) and (10). When executing the demanding combustion strategy "HCCl" with an expanded performance range, ductile iron is used 50 (GJS) or similar iron-based materials for the housing ring ( 2nd ) the entire work area is improved in terms of heat loss and expansion behavior. (Note [0028])

• z.B. mit 15 Brennräumen (8) und gleichsinniger Drehrichtung von Exzenterwelle und Gaswechselring (9) = Anzahl-4-Taktprogramme auf dem Gaswechselring (9) = 15/2 + 0,5 = 8, Antriebsuntersetzung für Exzenterwelle (7) zum Gaswechselring (9) : (15+1) :1→ beträgt 16:1.

In 7 the position of the gas exchange ring ( 9 ) with its planetary gear drive shown in the example of the 0.9 L 4-stroke engine. The assembly drawing 7 in section G - H gives an overview of the even distribution of all inlet and outlet channels ( 12th ) and ( 65 ) of the gas exchange ring ( 9 ) In the top third ( 9 ) as well as the sealing surfaces for the compression and expansion cycles, which the 4-cycle programs according to the number of ventilation chambers to be ventilated ( 8th ) and work rooms ( 3rd ) need:

• e.g. with 15 Combustion chambers ( 8th ) and the same direction of rotation of the eccentric shaft and gas exchange ring (9) = number of 4-stroke programs on the gas exchange ring (9) = 15/2 + 0.5 = 8, drive reduction for eccentric shaft ( 7 ) to the gas exchange ring (9): (15 + 1): 1 → is 16: 1.

The eccentric shaft drive ( 7 ) to the gas exchange ring ( 9 ) takes place via 3 fixed planetary gear sets with 3 steps to the internally toothed gas exchange ring ( 9 ), as explained here, with the steps: 2: 1 × 2: 1 × 4: 1 = 16: 1.

For the implementation of synchronous gas exchange flexibility for the metering of internal I-EGR or for the optimization of different combustion strategies and speed ranges, the position change of the gas exchange ring ( 9 ) the stepper motor adjustment ( 35 ) of the planet footbridge ( 34 ), which carries both stepped triple planetary gear sets or uses digitally controlled stepper motors to drive the gas exchange ring instead of the planetary gear sets. On the stepper motor ( 35 ) also the measurement of the drive torques ( 36 ) of the gas exchange ring ( 9 ) as a control variable for the sealing system of the gas exchange ring ( 9 ) eg by measuring the tangential forces on the planetary web ( 34 ) carried out. (see point [0017])

However, with only one gas exchange ring ( 9 ) independent inlet and outlet variations are dispensed with. (Point [0024] e)

The torque pulsation of the gas exchange ring drive due to the pulsating relief of the gas exchange ring ( 9 ) in the compression and expansion cycles is due to the large number of working chambers and the inertia of the gas exchange ring ( 9 ), compared to the pulsations of camshafts of the poppet valve drives, very low. This simplifies the dimensioning of the drive train with regard to dimensioning and noise development and makes it unnecessary to change intervals.

Solutions for the sealing systems

The sealing system is made easier with this engine because the transitions to be sealed are almost only flat, medium-temperature surfaces. The simple geometry allows low surface pressures with low sliding speeds of the sealing elements. These facilities also have a positive impact on the choice of economically viable materials, manufacturing processes and digital engine management.

For example, in our engine example with 0.9 L working space, the sliding speed between the gas exchange ring ( 9 ) and spiral band springs ( 14 ) in the side part ( 13g ) (With 15 Combustion chambers) in the range of only 2 ... 5 m / s at surface pressures of around 1 MPa.

• -Seitenteile (13)/Gehäusering (2) außerhalb der Kalotten und Brennräume mit Stahl-Federring (38) in „C“-Profil im Alu-Gehäusering (2) bzw. Eisenguss GJV.
• - Kühlwasserübergänge Gasgehäuse (16)/Seitenteile (13)/Gehäusering (2) drei Sätze 0-Ringe aus Kunststoff.
• - Öl-Gas-Gemischabsaugung (61)/(26) im Seitenteil (13öl) aus Gehäusering (2) ohne Dichtung, da innerhalb Stahlfederring (38).

In 2nd and 3rd we see the seals at rest:

• - Side parts (13) / housing ring (2) outside the calottes and combustion chambers with steel spring washer ( 38 ) in "C" profile in the aluminum housing ring ( 2nd ) or cast iron GJV.
• - Cooling water transitions gas housing ( 16 ) / Side panels ( 13 ) / Housing ring ( 2nd ) three sets of 0-rings made of plastic.
• - Oil-gas mixture extraction ( 61 ) / ( 26 ) in the side part ( 13 oil ) from housing ring ( 2nd ) without seal, because inside steel spring washer ( 38 ).

Oil-gas mixture extraction ( 61 ) / ( 26 ) from the eccentric ring ( 1 ) without seal, as extraction from lubricated sliding space ( 1 ) / ( 13 ).

• - Dichtsegmente (39) (11 bis 15) in den Einstichen auf den beiden Seiten des Exzenterringes (1) zwischen den Kalotten (5):
  • Diese Dichtsegmente haben die Aufgabe, nicht nur das Blowby zwischen Exzenterring (1) und Seitenteilen (13) zu vermindern bzw. völlig zu vermeiden, sondern sie müssen auch eine gasdichte Verbindung zu den Kalotten (5) herstellen.

sliding seals

• - sealing segments ( 39 ) ( 11 to 15 ) in the recesses on both sides of the eccentric ring ( 1 ) between the domes ( 5 ):
  • These sealing segments have the task not only of the blowby between the eccentric ring ( 1 ) and side panels ( 13 ) to reduce or completely avoid, but they must also have a gas-tight connection to the calottes ( 5 ) produce.

Comparable to the piston rings of reciprocating engines (annular gap!), The combustion chamber pressure can increase the spring preload ( 39d ) of the segments ( 39 ) for axial sealing against the side parts ( 13 ) reinforce ( 14 ). This is advantageous as a quasi self-regulating, load-controlled application reinforcement.

However, since at the same time the sealing contact must be as flat as possible and form-fitting to the calottes, each recess between the calottes ( 2nd ) Inserted sealing segments of the same thickness (39a + b). The slight tangential undersize of the arc length is used to secure it by an intermediate spring ( 39c ) to move tangentially against each other and thus a defined contact pressure in the form-fitting sealing contact surface to the calottes ( 5 ) to reach.

This ensures, on the one hand, that the sealing elements (39a + b) cannot wedge into the spherical cap contact, even when they are resting on the spherical cap, when the combustion chamber pressure is increased, but that they form-fit against the inner flank of the recess.

On the other hand, the combustion chamber pressure supports the segment on the combustion chamber side ( 39a ) by increasing the sealing pressures in the spherical cap contact surface and thus allows the required tightness to be generated despite the heat and tolerance-related gaps.

With the alignment of the defined, tangential contact pressure for the combustion chamber-side sealing segment ( 39a ) in the direction of the eccentric shaft rotation ( 7 ) ( 9 ) is due to the swiveling movement of the calottes ( 5 ) a more even loading of the sealing segments (39a + b) is achieved.

The axial preload of both sealing segments (39a + b) for the sealing contact to the side parts ( 13 ) is made possible by a recess-wide, steel C-profile spring ( 39d ) manufactured. This spring is in the longitudinal direction, that is tangential in the eccentric ring 1 between the domes ( 5 ), prestressed and used with little play (eg: <25 µm) to the width of the recess.

• Infolge der federnden Verschiebung der Dichtsegmente (39a+b) entstehen definierte brennraumseitige und exzenterrinnenraumseitige Spalte zwischen Segment (39) und Kalotte (5). Beide Spalte werden durch das C-Profil der Feder (39d) zum gasdruckführenden Kanal unter der Feder (39d) abgedichtet.

Both endings of these feathers ( 39d ) with C-profile are form-fittingly adapted for contact with the calotte ( 13 and 14 ):

• As a result of the resilient displacement of the sealing segments (39a + b), defined gaps between the combustion chamber and the eccentric interior are created between the segment ( 39 ) and calotte ( 5 ). Both gaps are identified by the C-profile of the spring ( 39d ) to the gas pressure channel under the spring ( 39d ) sealed.

For this purpose, the sealing segments (39a + b) lie flat on the flat side of the C-profile spring ( 39d ), the circular arc-shaped spring ends are positively adapted to the calotte contact and by the spring force of the incised middle part of the C-spring ( 39d ) defined under all operating conditions.

At the same time, the tolerance-related gap between the sealing segment on the combustion chamber side ( 39a ) to the puncture wall of the eccentric ring and the spring-related punctures ( 39e ) in the middle part of the C-spring ( 39d ) the pulsating combustion chamber gas pressure in the duct under the C-spring has a reinforcing effect. For the sealing contact between the sealing segments ( 39 ) and side panels ( 13 ) a positive pressure increase ( 14 and 15 ).

• - Dachfasenring (37) als Ölabstreifring: ein Ring pro Seitenfläche des Exzenterringes (1).

The pressure difference between the two flanks of the C-spring ( 39d ) at the same time there is full contact of the inner flank with the puncture wall of the eccentric ring ( 1 ) which produces the spring-related punctures ( 39e ) against gas leakage into the eccentric housing ( 31 ) seals off.

• - chamfer ring ( 37 ) as an oil scraper ring: one ring per side of the eccentric ring ( 1 ).

Isolating slide ( 4th ) with guidance through cylindrical domes ( 5 ): ( 3rd , 11 , 13 , 14 ) Slide valve ( 4th ) is a two-part in calottes ( 5 ) radial between eccentric ring ( 1 ) and housing ring ( 2nd ) guided rectangular plate, which, in its inclined parting plane by spring force ( 4d ) on the auxiliary slide ( 4b ) acting, axially sealing against the side parts (13g + oil).

On the housing ring end of the isolating slide ( 4b ) is the lead ( 4c ) to apply the leaf spring ( 4d ) and for diverting the oil-gas mixture to the gate valve-controlled oil drains ( 61 ).

By dimensioning the spring leaf ( 4d ) the sealing pressure between the separating slide ( 4th ) and side panels ( 13 ) set: approx. 50 N / cm ² (0.5 MPa) pressure is achieved by a spring force of 100 N. Both the sloping dividing surface and the sealing surfaces of the separating slide ( 4th ) against the side parts ( 13 ) are grooved for the lubrication and passage of a part of the extracted oil-gas mixture to the outer slide gate area in the housing ring ( 2nd ) and to the oil drains ( 61 ).

The separating slide ( 4a) are replaced by short bolts ( 4f ) in the calottes ( 5 ) the housing side ( 2nd ) held.

The eccentric ring end of the separating slide ( 4th ) runs with the two guide lugs ( 4g ) for dome guidance.

Calottes ( 5 ): In 12th the division and arrangement of the domes ( 5a ) u. ( 5b ) shown.

Since these cylinder sections (spherical caps) not only the separating slide ( 4th ), but also perform several sealing functions through extensive contact with the surroundings of the isolating slide ( 4th ) must be met, further divisions are required.

The quarter calottes are divided into ( 5a and 5b ) to accommodate the contact spring ( 5c ) for the alignment of the sealing surfaces to the side parts ( 13 ). ( 12th )

When compensating the thermal expansion difference, e.g. the aluminum alloy of the housing ring ( 2nd ) opposite the eccentric ring ( 1 ) resulting gap between the spring-loaded calotte quarters ( 5a ) and ( 5b ) (Order of magnitude 80 µm for extreme cold starts) are offset by the counter-calottes ( 5a ) and ( 5b ) sealed gastight.

The gas pressurization of the Kalottenviertel ( 5a ) u. ( 5b ) in addition to guiding the isolating slide ( 4th ) the flat gas seal between the slide valve ( 4th ), Eccentric ring ( 1 ) and housing ring ( 2nd ) and between the working chambers ( 3rd ), to the vacuum areas of the oil-gas extraction, to the eccentric housing ( 31 ) and to the tangential sealing elements ( 39 ). (see also 13 , 14 , 15 )

Due to the design-related wedge effect of the spherical caps, the radial gas pressures cause sealing pressures of 50 N / cm ² between all spherical caps and separating slide ( 4th ). For the targeted application at low gas pressures, the calotte quarters ( 5a , 5b) through the flat feathers ( 5d) radially biased. ( 12th , 13 u .14)

In 12th is the arrangement with asymmetrically divided domes ( 5 ) by the reference symbol ( 5c ) clarifies. Combustion chamber-side and inner counter spheres are asymmetrically divided (long ( 5a ), short ( 5b )) and are all due to the spring force ( 5c ) the side parts ( 13 ) on. The calotte divisions for the spring mount ( 5c ) are all in the area of the guide lugs ( 4g ).

Through the over the guide lugs ( 4g ) mutually arranged divisions, on the one hand the gas flow is sealed off and, on the other hand, the longer contact of the divisions with the guide lugs makes it easier to increase the eccentric size e.

Gas exchange ring ( 9 ): (Fig. 7)

• - im oberen Drittel zeigt der vergrößerte Ausschnitt (9) die Gaskanalöffnungen Einlass (12) und Auslass (65) zu den Brennkammern (8). Hier ist auch die Anordnung der 8 kegeligen Segmente (18) für die Zentrierung des Gaswechselringes (9) dargestellt.
• - das im Urzeigersinn folgende Drittel in 7 zeigt einen tiefer liegenden Schnitt durch die Leiterstruktur der Kühlwasserführung zu den Brennkammern (8) im Seitenteil (13g) mit den dazu gehörigen Einlassverschraubungen (24),
• - das dritte Segment zeigt mit der Außenansicht des Gasgehäuses (16) die Zu- und Ableitungen für Einlassluft bzw. -gas (41), Kühlwasser ein (24), Abgas (33) und Austritt für das Öl/Gas-Gemisch (63),
• - im Zentrum des Querschnittes sind dargestellt: der 3-fache Planetensatz (15) zum Antrieb des Gaswechselringes (9) mit dem drehbaren Planetensteg (34) zur Verstellung (35) der Gaswechselzeiten. Auch sind hier die Positionen der acht Aktuatoren (19) für die Anstellung des Gaswechselringes (9) und die Öleinlässe primär (27) für Gasgehäuse (16) und sekundär (28) für die Öl-Gasgemischversorgung der Exzenterseite (31) angegeben.

7 shows in addition to the longitudinal section through the engine a sectional view across various elements of the gas side (gas housing ( 16 )):

• - the enlarged section shows in the upper third ( 9 ) the gas channel openings inlet ( 12th ) and outlet ( 65 ) to the combustion chambers ( 8th ). Here is also the arrangement of the 8 tapered segments ( 18th ) for centering the gas exchange ring ( 9 ).
• - the third in clockwise direction in 7 shows a deeper section through the conductor structure of the cooling water supply to the combustion chambers ( 8th ) in the side part ( 13g ) with the associated inlet fittings ( 24th ),
• - the third segment shows the external view of the gas housing ( 16 ) the supply and discharge lines for inlet air or gas (41), cooling water ( 24th ), Exhaust gas ( 33 ) and outlet for the oil / gas mixture ( 63 ),
• - in the center of the cross section are shown: the triple planetary set ( 15 ) to drive the gas exchange ring ( 9 ) with the rotating planetary bridge ( 34 ) for adjustment ( 35 ) the gas change times. The positions of the eight actuators ( 19th ) for the adjustment of the gas exchange ring ( 9 ) and the oil inlets primary ( 27 ) for gas housing ( 16 ) and secondary ( 28 ) for the oil-gas mixture supply on the eccentric side ( 31 ) specified.

• der Ring hat den Einlasskanal (12) gerade mit der Brennkammer (8) der Arbeitskammer XV. in Deckung gefahren.

To the top third of the 7 : The arrangement of the inlet channels ( 12th ) and the outlet channels ( 65 ) shows the function of clockwise with the eccentric shaft 7 rotating gas exchange ring ( 9 ):

• the ring has the inlet channel ( 12th ) straight with the combustion chamber ( 8th ) of the Chamber XV. took cover.

In the circle section between the working chambers I. and III. there is a complete 4-stroke program from the end of compression in III., half of the gas exchange carried out with the outlet and the inlet channel entering ( 12th ) in II. and the subsequent sealing surface of the compression stroke, which ends with the start of combustion in combustion chamber I.

It becomes clear that with the 4-stroke process an ignited combustion chamber ( 8th ) is surrounded in each case by gas-changing chambers.

Basically, the arrangement of the gas exchange channels in the gas exchange ring ( 9 ) Combustion processes that deviate from the "Otto process", such as the 2-stroke-like "Z process", are also possible, of course with a different number of programs and corresponding drive ratios for the gas exchange ring. (Z-HCCI engine from Aumet Oy, Finland). All successive combustion chambers can be ignited when activated and even numbers of chambers can be used.

Because of the importance, the normal 4-stroke process, which also covers the "diesel process", is shown in this application.

Here are the inlet and outlet channels in their 4-stroke sequence on the gas exchange ring ( 9 ) arranged in a circle and form with the contact sliding surfaces ( 9k ) of the gas exchange ring ( 9 ) the 4-stroke programs required for the selected number of work chambers. Only with an odd number of compartments can the 4-cycle process run evenly.

With the number of chambers used here = 15 and synchronization of the eccentric shaft ( 7 ) and gas exchange ring ( 9 ) 15/2 + 0.5 = 8 four-stroke programs (inlet - compression - expansion - outlet) are even in the gas exchange ring ( 9 ) arranged.

The gas exchange ring ( 9 ) together with the creation and sealing of the work rooms by the separating slide ( 4th ) the basis for the invention.

• Die Lagerung des Gaswechselringes (9) (Basiswerkstoff GG oder Keramik) wird von mindestens einem axialen Kugellager (21) am innenverzahnten Antriebsrad des Planetenradsatzes (15) geführt.

The gas exchange ring ( 9 ) shows the enlargement of the longitudinal section in 8th :

• The storage of the gas exchange ring ( 9 ) (Base material GG or ceramic) is supported by at least one axial ball bearing ( 21 ) on the internally toothed drive wheel of the planetary gear set ( 15 ) guided.

The contact sliding surface slides on the hot side ( 9k ) of the gas exchange ring ( 9 ) on the sealing surface of the side part ( 13g ) and carries on the inlet side ( 41 ) two axial labyrinth sealing rings with compressed air application ( 23 ) in the gas housing ( 16 ) Separate the exhaust and inlet spaces from each other and seal them at the same time. The gas exchange ring ( 9 ) perform the required thermal expansion (for GG material) of approximately 0.40 mm radially, which due to its medium temperature places stress on it due to the simultaneous flow of exhaust gases and fresh air, without interfering with the function of the axial labyrinth seals or taking them rotating . For this purpose, the axial labyrinth sealing rings ( 23 ) of pins in the puncture base of the gas housing ( 16 ) held against the tendency to rotate, as is known from piston rings of 2-stroke reciprocating piston engines.

To compensate for this thermal expansion, the gas exchange ring ( 9 ) opposite the drive wheel ( 15 ) slide radially in relation to its mounting position. For this, the gas exchange ring ( 9 ) on the ball-bearing drive wheel ( 15 ) with e.g. 8 resilient screw connections ( 17th ) centered and each by the balls ( 20 ) taken free of play. Centering the gas exchange ring ( 9 ) is due to the evenly around the circumference of the drive wheel ( 15 ) spring-loaded tapered segments ( 18th ) updated. The centering therefore also occurs when the gas exchange ring cools down ( 9 ) back again.

Three sealing systems ensure the function of the gas exchange ring ( 9 ).

• 1. Trennung von Abgas- und Einlassraum: durch zwei Labyrinth-Dichtringe mit Druckluftanlegung (23) im Gasgehäuse (16).
• 2. Abdichtung der Überführung von Einlassluft und Abgas zwischen Gaswechselring (9) und Seitenteil/Brennräume: um die Brennkammeröffnungen (22)angeordnete Spiralbandfedern (14), die unter Vorspannung die Brennkammeröffnungen (8) gegen die Kontaktgleitfläche (9k) abdichten. (10) Dazu liegen die Spiralbandfedern (14) mit mindestens zwei Federbandwindungen für die federnde Eigenschaft kegelig vorgeformt, kreisrund- und plangeschliffen in kreisrunden Einstichen um die Brennraumöffnungen (22) zentriert. Die innere Windung der Spiralbandfedern (14) gleitet dabei auf der Gaswechselring-Fläche und die äußere Windung der Spiralbandfedern (14) trägt auf der ganzen Stirnfläche im Einstichgrund.

For this purpose an enlargement of the gas exchange ring environment in 2a u . 2c :

• 1.Separation of exhaust and inlet space: through two labyrinth sealing rings with compressed air ( 23 ) in the gas housing ( 16 ).
• 2. Sealing the transfer of intake air and exhaust gas between the gas exchange ring ( 9 ) and side part / combustion chambers: around the combustion chamber openings ( 22 ) arranged spiral band springs ( 14 ) that pretension the combustion chamber openings ( 8th ) against the contact sliding surface ( 9k ) seal. ( 10th ) There are coil springs ( 14 ) with at least two spring band coils pre-shaped for the resilient property, circular and plane ground in circular recesses around the combustion chamber openings ( 22 ) centered. The inner turn of the coil tape springs ( 14 ) slides on the gas exchange ring surface and the outer winding of the spiral band springs ( 14 ) bears on the entire end face in the puncture base.

When the combustion chamber pressures act on the inside of the spiral band springs, the windings of the spiral band springs (due to the surface conditions in the dynamic pressure build-up at the spring band width and band end face) 14 ) pressed together and thus the resilient pre-tension caused by the regulated application pressure of the gas exchange ring ( 9 ) is superimposed when operating the motor. This ensures that the friction properties of the materials sliding in dry running (eg steel hardened against GG) are not overused by the high combustion chamber pressures.

Since the function of the spiral band springs ( 14 ) plays in pulsating dynamic operation, the rhythmic load change on the spiral coil spring windings ensures the sealing application on the gas exchange ring surface.

• - zum einem wird die Kontaktgleitfläche (9k) in einem der letzten Arbeitsgänge in einem mittleren betriebsnahen Warmzustand plangefinisht, um einen großen Anteil, der im variablen Betrieb der Brennkraftmaschine auftretenden Wellen und Konizitäten der Kontaktgleitfläche (9k) zu vermeiden.(ggf. vor einer verschleißhemmenden keramischen Dünnbeschichtung)
• - zum andern wird die Federsteifigkeit der kegeligen und mehrwindigen Spiralbandfeder (14) unter Berücksichtigung ihrer Eigenfrequenz so dimensioniert, dass ihre Kontaktflächen auch bei geringer Anpressung der Kontaktgleitfläche (9k) des Gaswechselringes (9) folgen. Die sehr verschiedenen Massen und Elastizitätsmoduln von Spiralbandfedern und Gaswechselring liefern nicht nur die erwünschten Differenzen in den Eigenfrequenzen, sondern mindern auch die Strukturanregung zu hohen Reibwerten und damit zu Verschleiß.

In order for this rhythmically sealing application of the spiral band springs also on the long-wave contact sliding surface due to operational heat deformations of about 10 to 20 µm ( 9k ) of the gas exchange ring ( 9 ) can follow safely, two additional measures are carried out:

• - on the one hand, the contact sliding surface ( 9k ) in one of the last work steps in a medium-level warm state close to the plan, by a large proportion of the waves and conicity of the contact sliding surface that occur during variable operation of the internal combustion engine ( 9k ) to avoid (possibly before a wear-resistant ceramic thin coating)
• - on the other hand, the spring stiffness of the conical and multi-wind spiral coil spring ( 14 ) dimensioned taking into account their natural frequency so that their contact surfaces even with little contact pressure on the contact sliding surface ( 9k ) of the gas exchange ring ( 9 ) consequences. The very different masses and moduli of elasticity of spiral band springs and gas exchange rings not only provide the desired differences in the natural frequencies, but also reduce the structural excitation of high friction values and thus wear.

• - die Vorspannung der Spiralbandfeder (14) (10) eingehalten,
• - Gasdichtheit,
• - die Reibverluste vermindert (bei Volllast ca. 500 W beim Ausführungsbeispiel 0,9 L)
• - und der Verschleiß der trocken laufenden Bauteile minimiert.

The 3rd . System provides the regulation of the application pressure of the gas exchange ring ( 9 ) opposite the side part ( 13g ) In addition to the safe sealing of the combustion chambers, this control loop has the task of dimensioning the contact pressure in such a way that the full-surface contact of the gas exchange ring ( 9 ) - side part ( 13g ) in the contact sliding surface ( 9k ) is achieved with a minimum of the resulting surface pressure. For this contact quality, the following requirements for which the reference variable of the control loop ( 17th ) ensures, realizes:

• - the pre-tension of the spiral band spring ( 14 ) ( 10th ) adhered to
• - gas tightness,
• - the friction losses are reduced (at full load approx. 500 W in the embodiment 0.9 L)
• - and minimizes wear on dry-running components.

The operating point-dependent electrical current as the manipulated variable of the 8 electro-magnetic actuators ( 19th ) which the ball bearing ( 21 ) has the task, on the controlled system, namely in the contact sliding surface ( 9k ) to generate precisely the pressure which, when the two surfaces are applied smoothly, only the flush, resilient pre-tensioning of the coil band springs SBF ( 14 ) + Reserve causes.

The logical connection of the manipulated variable "actuator pulse (19)", which is linked to the disturbance variables such as fuel rate, supercharger pressure on the inlet side of the gas exchange ring ( 9 ) as well as speed and number of active working chambers ( 3rd ) (ZFW) is constantly adjusted and with which the gas exchange ring ( 9 ) against the side surface ( 13g ) is pressed, leads to the result of the controlled system (contact sliding surface ( 9k ), namely the controlled variable, which depends on the course of the torque for driving the gas exchange ring ( 9 ) is pictured. ( 17th and 18th )

This regulated, low-delay assurance of the quality of the gas exchange ring side part contact ( 9k ) is decisive for operational safety with regard to the reciprocal behavior of the gas exchange ring drive torque at the fuel rate or engine load. The schematic example of a torque curve and the underlying column and forces between the gas exchange ring ( 9 ) and side part ( 13g ) depending on different operating conditions 18th . The impact of the knocking operation of individual combustion chambers ( 8th ) can be seen.

One of the most important disturbance variables regarding the contact conditions in the contact sliding surface ( 9k ) is the supercharger pressure on the inlet side of the gas exchange ring ( 9 ). ( 17th ) In the selected embodiment with the working space size 0.9 L and an area of the inlet side of 250 cm ² , between the labyrinth sealing rings ( 23 ), the charge pressure is in the range 1 to 3 bar => 0.1 to 0.3 MPa. required contact force reached.

Here, the supercharger pressures, which correlate very clearly with the combustion pressures, provide a dynamic, practically self-regulating part of the application forces to be used in the control loop. However, in order to regulate the electro-magnetic actuators ( 19th ) the inlet surface of the gas exchange ring ( 9 ) so that at least 40% (e.g. approx. 2500N) of the application force is applied to the actuators ( 19th ) are available as a work area.

On the gas exchange ring ( 9 ) acting axial forces from a helical toothing of the planetary drive ( 15 ) are a self-regulating component, the dynamic behavior of which under various load conditions, such as abrupt load reduction, for example due to the slight inclination of the toothing in terms of the controllability and the dominance of the electromagnetic actuators ( 19th ) must be taken into account.

The disturbance variables mentioned, which act on the manipulated variables and are related to each other, allow the control algorithm to be permanently taught in the many changing operating states, so that we can speak here of the use of artificial intelligence.

The course of the friction relationships between the gas exchange ring ( 9 ) and side part ( 13b ), which is very sensitive due to the drive torque of the gas exchange ring ( 9 ) is shown, not only shows the desired contact conditions on the side part ( 13g ) and controls the correct behavior of the spiral band springs ( 14 ), but leads to correct, low-delay readjustment of the high contact pressures of the actuators ( 19th ) on the circumference of the ball bearing ( 21 ) even if there is a sudden decrease in performance.

An additional advantage is the ongoing control of the condition on the gas exchange ring ( 9 ), which also means the starting conditions for the spiral coil springs at every start ( 14 ) can be determined automatically, namely from the drive torque of the gas exchange ring ( 9 ) in the short period of the start-up with: e.g. the reference variable for the control loop ( 17th ) the "target torque on the gas exchange ring ( 9 ) = at max. Spiral band spring travel + 10% reserve. “That means that each time the machine is started, this is due to the pretension ( 19a ) generated drive torque of the gas exchange ring ( 9 ) as an initial measurement for the quality in the contact sliding surface ( 9k ) between gas exchange ring ( 9 ) and side part ( 13g ) is won. The slight, brief drop (max. 30 ms at start) of the gas exchange ring drive torque when the machine starts is confirmation for the engine management and control unit that the dynamics of the control algorithm are well set.

The transition from contact to pure contact of the coil springs ( 14 ) in the contact sliding surface ( 9k ) for sliding on the entire contact sliding surface of, for example, 350 cm ² is registered by a change in the torque gradient = f (contact force).

Cooling and lubrication system

The water circuit of the cooling system is characterized by the axial flow through all four ring or disk-shaped housing parts. ( 7 and 8th )

In order to reduce temperature differences between the individual parts, the cooling water comes out of the ring line ( 24th ) into the gas housing, where it also cools the intake air and possibly the externally recirculated exhaust gas EGR, flows around in the gas-side part ( 13g ) via ring distributor ( 24a ) u. ( 24b ) the combustion chambers ( 8th ), flows through evenly in the housing ring GR ( 2nd ) distributed cooling water rooms and is after the flow of the side part ( 13 oil ) via the ring line ( 25th ) returned to the heat exchanger.

The three transitions between the 4 parts are sealed with elastic O-rings.

The oil circuit of the lubrication and cooling system is divided into two sub-circuits, namely the gas exchange side ( 16 ) with the drive (15) + bearing ( 21 ) of the gas exchange ring ( 9 ) and in the eccentric side ( 31 ) with the eccentric drive including isolating slide ( 4th ) with the calottes ( 5 ), divided up. ( 1 , 2nd and 3rd )

The parallel connection of the partial oil circuits is used for the supply of pressure oil to slide bearings as the main and eccentric ring bearings ( 29 ) and ( 30th ) used, which have a central bore in the eccentric shaft ( 7 ) with pressure oil ( 42 ) must be supplied.

When using plain bearings (with a summer field number close to 10!) For main and eccentric bearings, which instead of the roller bearings cause greater friction losses, larger sliding gate and caliper loads as well as limit loads on the bearing coating at full load and higher speeds (peripheral speeds> 50 m / s) a gear pump ( 42 ) with higher oil pressures from the settling tank, the bearing points due to the eccentric shaft drilled for this variant ( 7 ).

In the case of roller bearings (e.g. cylindrical roller bearings) for the bearings ( 29 ) u. ( 30th ) With the series connection of the oil circuits, the pressure oil pump ( 42 ), since a mist-like mixture is created by swirling the inflowing or sucked-in oil and gas components with good lubrication and cooling properties. For the lubrication and cooling of the flowed roller bearings ( 29 ) u. ( 30th ) this oil-gas mixture is optimally effective at high loads and high speeds.

Oil circuits in parallel for dry sump systems, schematically in 19th When connecting the oil circuits in parallel from the gas exchange side ( 16 ) and eccentric side ( 31 ) the planetary gear set ( 15 ) ( 7 and 11 ) of the gas exchange ring drive with oil from the controllable oil distributor ( 43 ) via the oil distributor ring ( 27 ) flooded. In the gas housing ( 16 ) supplies the oil with the formation of an oil-gas mixture both the 3 stepped planetary gear sets ( 15 ) with the internally toothed drive wheel, as well as the axial ball bearing ( 21 ). At the same time, this oil-gas mixture also cools the inner surface of the slow-moving gas exchange ring ( 9 ), from where it is collected through the conical shape of this surface, through the recesses in the gas exchange ring flange and through the thrust ball bearing ( 21 ) to the drain opening ( 63 ) in the lower part of the gas housing ( 16 ) flows. The return to the settling tank ( 44 ), which is also the oil cooler ( 49 ), occurs due to the excess pressure in the gas housing ( 16 ). (see also 3rd )

In parallel to the gas housing ( 16 ) connected eccentric side ( 31 ) hits the oil distributor rings ( 28 ) of the side parts ( 13 ) supplied oil after flowing through the two main bearings ( 29 ) on the outer flanks with the counterweights of the eccentric shaft ( 7 ). From the counterweights of the eccentric shaft ( 7 ) swirled, the oil-gas mixture flows into the eccentric interior ( 31 ) and the eccentric bearing ( 30th ), from which the oil-gas mixture is uniformly distributed in the eccentric ring ( 1 ) arranged check valves ( 32 ) of the pumping action of the separating slide-calotte system ( 4th ) / ( 5 ) and the oil suction pump ( 45 ) via the oil ring line ( 26 ) in the settling tank ( 44 ) is returned. The individual check valves are flutter valves in the 3-part ring segment ( 32 ) arranged ( 3rd and 8th ). The flutter valves are suitable for extracting the eccentric housing ( 31 ) at pulse frequencies around 100 Hz.

The oil-gas mixture is extracted via the radial bores in the eccentric ring ( 1 ), which also serves as the outlet space for the separating slide lugs ( 4g ) act.

The eccentric bearing ( 30th ) as a cylindrical roller bearing, the oil-gas mixture flows intensely, as the one-sided position of the oil drains ( 61 ) in the side part ( 13 oil ) a partial flow through the roller bearing ( 30th ) sets. The extraction of the oil-gas mixture via the oil drains ( 61 ) due to the negative pressure in the ring line ( 26 ) (Suction pump ( 45 )) the separating slide ( 4th ) whose pumping effect is in the order of 100 L / min depending on the number of working chambers, engine volume and speed.

The influence of pulsation on the flow through the separating slides to be cooled and lubricated ( 4th ) also promotes the lubrication and cooling of all domes ( 5 ) and sealing elements such as the inclination of the separating slide ( 4b ).

The negative pressure in the ring line ( 26 ) exists due to the gate valve-controlled oil drains ( 61 ) permanently at the level of the control unit ( 54 ) required values. Due to the negative pressure in the ring line ( 26 ) in addition to the safe extraction of the oil-gas mixture from the eccentric housing ( 31 ) the influence on the lubrication, gas and pressure conditions in the sliding and guiding surfaces on both sides between the eccentric ring ( 1 ) and side panels ( 13 ) by the gate valve-controlled oil drains ( 61 ) and the inclusion of the relief drilling ( 62 ) of the eccentric ring ( 1 ) reached.

Oil circuits in serial connection Fig. 20

Alternatively, the large delivery potential of the separating slide calotte system (TS-KL system) is used to provide both the necessary oil supplies and the suction of the gas components of the blow-by and the labyrinth air with the two oil circuits connected in series on the gas and eccentric sides perform.

Taking into account the blowby proportions from gas exchange and eccentric operation and the labyrinth air ( 23 ) of the gas housing ( 16 ) with 0.3 to 1.5 liters of gas-oil mixture per second, depending on the speed and load for our engine example of 0.9 L working space, the pumping capacity of the isolating slide calotte system is 1.5 to 4 L / s (mean values at normal pressure) for additional tasks such as for cooling the highly loaded eccentric ring ( 1 ) used [0021].

The suction pump ( 45 ) in the settling tank ( 44 ) for excess pressure which is generated by the valve switched by the control unit ( 56 ) is kept at the required values.

From the settling tank ( 44 ) the required oil flow via oil valve ( 47 ), Filter ( 48 ) and oil distributor ( 27 ) the planetary gear set ( 15 ) of the gas housing ( 16 ), Gas exchange ring ( 9 ) and thrust ball bearings ( 21 ) supplied with the filtered and cooled oil from the settling tank centrally axially ( 27 ) in 7 .

The negative pressure due to the intensive suction effect of the separating slide relative movement including the oil suction pump ( 45 ) sucks the oil sump of the gas housing ( 16 ) together with gas components and supplies via the oil cooler ( 49 ), the temperature sensor ( 51 ) and the pressure sensor ( 50 ) via the two oil distributor rings ( 28 ) the two main camps ( 29 ) of the eccentric shaft ( 7 ) and the rolling bearing ( 30th ) of the eccentric ring ( 1 ).

From the eccentric housing ( 31 ) to the radial passages of the eccentric ring ( 1 ) via the check valves ( 32 ) to the sucking gate valve system, the oil circuit closes via the gate valves controlled by the gate valve ( 61 ) to the oil collection ring ( 26 ) and via temperature sensor ( 52 ), Flow meter ( 53 ), Pressure sensor ( 60 ) and suction pump ( 45 ) to the settling tank ( 44 ).

In addition to the gas components blowby and labyrinth air, this is used by the control unit ( 54 ) switched ventilation valve ( 55 ) on the gas housing ( 16 ) to secure and limit the required negative pressure in the interior of the gas housing ( 16 ) and the eccentric housing ( 31 ).

As already described in [0021], the negative pressure in the ring line ( 26 ) in addition to the safe extraction of the oil-gas mixture from the eccentric housing ( 31 ) the influence on the lubrication, gas, temperature and pressure conditions in the sliding and guiding surfaces on both sides between the eccentric ring ( 1 ) and side panels ( 13 ) through the slide valve-controlled oil openings ( 61 ) and the inclusion of the relief drilling ( 62 ) of the eccentric ring ( 1 ) reached.

The operation of the oil-gas mixture conveyance on the basis of the reliable isolating slide vacuum for the entire oil circuit not only makes it possible to dispense with oil pumps, but also, as when operating with oil pumps [0019 u. 0021], the continuous use of the oil and gas components from the analysis of the two sub-circuits for regulating and monitoring the important data such as oil consumption and blowby development of the sub-circuits of the internal combustion engine.

The analysis of the partial circuits on the gas exchange side and eccentric side of both oil circuit circuits processes in the control unit ( 54 ) the respective pressures ( 50 ), ( 57 ), ( 60 ), Flow rates ( 50 ), ( 53 ), incoming and outgoing temperatures ( 44 ), ( 51 ), ( 52 ) of the sub-circles as well as oil level and blowby quantities from the settling tank ( 44 ).

An advantage for the operational safety of the internal combustion engine is the use of a control system that goes beyond the effect of a simple control of the oil circulation with the command variable temperature (temperature control) with the additional command variables oil quantity difference and gas proportion as well as the control variables oil flow and oil mist vacuum in the rooms ( 16 ), ( 31 ) u. ( 26 ).

Likewise is the influence described in [0022] on the lubrication, gas, temperature and pressure conditions in the sliding and guiding surfaces on both sides between the eccentric ring 1 and side panels ( 13 ), ie influencing the sliding gap between the sealing segments ( 39 ) and the roof chamfer rings ( 37 ), due to the gate valve-controlled oil drains ( 61 ) and the inclusion of the relief drilling ( 62 ) of the eccentric ring ( 1 ) reached.

In addition, the separate recording of the respective gas portion leads us to more precise control of the tightness and material wear on the gas exchange ring ( 9 ) and on the separating slides ( 4th ).

The exhaust gas recirculation ( 56 ) after the oil separation forms, in addition to the pressure control of the settling tank ( 44 ), together with the required amounts of external EGR, the sometimes large proportion of E-EGR, especially when operating with low ZFW numbers. ([0024] d)

Combustion process strategies

The properties of the internal combustion engine according to the invention, such as effective separation of the effective, compact combustion chamber ( 8th ) from the expansion space ( 3rd ) (Point [0004] as well as small, inexpensive work spaces ( 3rd ) large number of cast iron GJS and GJV, enable different combustion process strategies. Since the heat of combustion is only in the gas housing ( 16 ) must be removed more intensively, come for the combustion and working chambers ( 8th ) and (3) effectively use cast iron materials such as GJS and GJV, which allow 6 times lower heat losses than aluminum alloys. The use of electrically operated chargers (gas blowers) influences the strategy of the combustion process.

Regarding the sensibility of the electrically operated charger, it should be noted that the independence of the boost pressure from the condition, energy and availability of the exhaust gases to influence the filling status of the combustion chambers ( 8th ) is very advantageous in terms of pressure and chemical composition compared to the possibilities of complicated variations in gas exchange times. This is particularly the case with loader tasks outside of the pure specific increase in performance of the internal combustion engine, such as with exhaust gas optimization and continuous bridging of power levels during ZFW operation without throttling.

1. a) Überwiegende Verbrennung vorgemischten Brenngases infolge der intensiven Verwirbelung der beim Einlass- und Kompressionsanströmen der kleinräumigen Brennräume eingespritzten Kraftstoffe bei in Einlass- und/oder Kompressionstakt unterteilte Einspritzimpulsbreite.
2. b) Entfall der Drosselung zur Leistungssteuerung durch Kraftstoff-Einspritzung nur in der benötigten Anzahl von im optimalen Betriebspunkt betriebenen Brennkammern (8) - Arbeitskammern (3).

The following properties of the internal combustion engine are based on these principles:

1. a) Predominant combustion of premixed fuel gas as a result of the intensive swirling of the fuels injected when the intake and compression flow into the small-scale combustion chambers with an injection pulse width divided into the intake and / or compression stroke.
2. b) Elimination of throttling for power control by fuel injection only in the required number of combustion chambers operated at the optimal operating point ( 8th ) - working chambers ( 3rd ).

The order of the working chambers ( 3rd ) selected so that all existing chambers ( 3rd ) work in an even firing order, "ZFW" firing order selection.

in the selected example with [0001] 15 Chambers is the firing order: 1-9-2-10-3-11-4-12-5-13-6-14-7-15-8-1 for the 25% power. It will be here 3rd Activatable chambers without fuel supply omitted: each 4th . 25% of the possible chambers are supplied with fuel. Control effort: software in engine management, switching from one firing order stage to the next is possible from one working chamber to the next.

The periodically fuel-free working chambers ( 3rd ) essentially only lose friction losses as gas pumps, like the well-known partially-switching reciprocating piston engines, but they recover compression energy through the heat transfer from the flushed combustion and working chamber walls. These periodically air-pumping working chambers ( 3rd ) contribute to the damped, low-vibration running of the engine and are all permanently in operational condition.

The alternately active operation of the working chambers ( 3rd ) at partial load, by influencing the exhaust gas composition and temperatures, the setting of the gas change times and in particular the E-EGR shares for auto-ignition operation are expanded. In addition to the achievement of practically continuous power control, there are: use of the electric charger, variation of the EGR portion and earlier ES <60 ° NDC at low engine speeds.

The associated control loop (closed loop) in engine management simultaneously uses these manipulated variables to maintain the optimal operating point ([0024]).

Regarding the choice of the electrically operated charger, it should also be noted that the independence of the boost pressure from the condition, energy and time span of the exhaust gases not only affects the filling level of the combustion chambers through the possibilities of complicated variations in gas exchange times, but also so-called "turbo holes" as well Avoiding problems when starting under HCCI conditions.

c) With regard to their CO ₂ - NOx - fine dust - consumption and speed characteristics, the working chambers can always be regulated to the optimum operating point.

The mixing, diffusion speed and quality of fuel with air and internal and external EGR for optimal homogeneity of the fuel gas is not only dependent on the gas turbulence in the injection area of the combustion chamber ( 8th ), but also from the gas temperature and the jet volume, which is the required fuel injection quantity per combustion chamber ( 8th ) and clock required. The gas temperature is mainly in the intake cycle in addition to the wall temperatures of the geom. Compression ratio and the unthrottled air-gas supply dependent. Both are in the combustion chamber according to the invention ( 8th ) to be assessed positively: the chamber walls are inexpensive due to the iron materials used and large delivery rates lead to the selected geom. Compression ratios in addition to the excellent turbulence properties at high gas temperatures. When injecting in the compression cycle there is no lack of evaporation with regard to the temperature and with combustion chamber volumes of 5 cm ³ with fuel rates in the range of <5 mm ³ per work cycle and combustion chamber ( 8th ) follow the shortest beam diffusion times of <1ms with suitable fuels.

All prerequisites for the use of perfect combustion with excellent CO ₂ , NOx, particulate matter and consumption values are given.

Can the use of all of these good conditions for intensive, homogeneous mixture formation for the diesel process be a gain?

The optimized injection at the end of the compression cycle to the concentrated, squish-assisted, self-igniting flame front is of great advantage for the diesel operation of the engine according to the invention. The rate of a homogeneously swirled pilot injection during the low temperatures of the intake stroke and / or during the start of compression only increase to the limit of stratification (soot limit) or early ignition of the fuel gas.

The successful combustion of these combined fuel distributions, with relatively low λ values <1.3 and large values of the EGR proportions> 30% for diesel use, enables a more extensive binding of oxygen through the more intensive assignment of the oxygen to the diesel oil molecules and thus the reduction of NOx levels in the exhaust gas. Evenly lowering the combustion temperature during ZFW operation brings advantages for NOx reduction.

Here is the effective control of the ignition timing by varying the EGR as a manipulated variable and with the auto-ignition timing from the analysis of the seismic signal ( 46 ) (sa [0029]) is required as a controlled variable.

• → vorgemischtes homogenes Brenngas
• → Arbeitskammer-Zündfolgenwahl, ZFW
• → hocheffiziente Verbrennung in kleinen kompakten Brennräumen

führt mit AGR >20% + elektrischen Lader + geom. Verdichtung 12...16 + Regelkreis zur sicheren Kompressionszündung mit den Stellgrößen: Laderdruck, E-AGR + I- AGR-Rate (Variation der synchronen Gaswechselzeiten) + Einspritz-Timing mittels Auswertung des Klopfsignals aus der Analyse des seismischen Gebersignals (46) oder anderer Signale. (s.a. [0029])d) Extended HCCI operation by combining operating modes a, b and c:

• → premixed homogeneous fuel gas
• → Working chamber ignition sequence selection, ZFW
• → highly efficient combustion in small, compact combustion chambers

leads with EGR> 20% + electric charger + geom. compression 12th ... 16 + control circuit for safe compression ignition with the manipulated variables: supercharger pressure, E-EGR + I-EGR rate (variation of the synchronous gas exchange times) + injection timing by evaluating the knock signal from the analysis of the seismic transmitter signal ( 46 ) or other signals. (see also [0029])

Started with electrical ignition sparks and throttle-free with a small number of chambers, for example on the 0.9 L machine, with a number of working chambers 15 in every 8th chamber fuel is very late 45 ° n. LOT - in the intake tract - injected for very large λ, with electric charger with 0.15 MPa.

As soon as the compression ignition is reached with EGR, fuel gas temperature and ignition delay, the optimal operating characteristic, which has now been learned in engine management, is used in the load-dependent working chambers with the electrical ignition spark still active.

At idle, for example, only with every 11th chamber, ie at 15 Chambers, with less than one chamber per revolution with the ignition injection sequence: 1-8-15-7-14-6-13-5-12-4-11-3-10-2-9-1. The load requirements in an operated vehicle are not only taken into account automatically by the choice of a suitable gear, for example, but the appropriate number of combustion chambers is automatically switched on ( 8th ) added. Effects of operating small numbers of working chambers per revolution with the ZFW working chamber ignition sequence described above, such as the strong enrichment of the air content in the exhaust tract, are compensated for by setting the gas exchange times earlier. In order to maintain the required high internal EGR rate during HCCI operation, the outlet closes earlier and the inlet opens earlier, thereby reducing the influence of oxygen and the delivery losses of the electric charger due to the higher exhaust gas pressure during the overlap phase. ( 21 )

e) The gas exchange device gas exchange ring ( 9 ) of the internal combustion engine described so far is due to the interdependent, firmly integrated gas exchange channels ( 12th ) and ( 65 ) for inlet and outlet on a ring limited to synchronous variation of outlet and inlet times by varying the web position.

Apart from the simplicity of the associated planetary drive ( 15 ) and the common control option for contact pressure and storage, the effort of a variable gas exchange device is included 2nd Gas exchange rings, which in addition do not solve tightness problems due to the different temperatures of the two separate gas exchange rings, are so large and unsafe that the pursuit of this possibility has been refrained from.

By using the electric charger, using the synchronous variation of the gas exchange times, application-specific programs on the gas exchange ring and the consistent load control with the working chamber - ignition sequence selection ZFW, the required goals can be achieved.

1. A) Der Einsatz als Range-Extender ist aufgrund der punktgenauen Betriebsweise als Akkulader vorteilhaft für Effizienz, Aufwand und Schadstoffe zu konzipieren: Keine ZFW, die Regelung für Gaswechselringanlegung entfällt, da bei dieser Betriebsart mit konstantem Brennkammerdruck gearbeitet wird. Auch die Regelung zur Ölnebelabsaugung kann vereinfacht auf die Führungsgrößen Temperatur und Menge beschränkt werden, da auch hier die gleichförmige Betriebsweise verwertbare Messdaten aus dem Verhalten von Temperatur und Absaugmengen generiert. Kraftstoff: Benzin 90 Oktan, Arbeitsraum: ca.600 cm³, n=3000U/min, Kammerzahl 9, e= 6 mm, Verdichtung: 10, ohne Drosselung, ohne Lader, P =25 kW, Außen-Durchmesser ca. 350 mm, Kammerlänge= 80 mm, Gesamtlänge ca. 200 mm. Gewicht: ca.50 kg, Zündung mit Zündkerze, λ=1. Einspritzen im Einlass-Takt: 45° n. LOT, interne AGR durch AS: 15°n.LOT, EÖ: 15° v. LOT, übrige Ventilsteuerzeiten: AÖ: 10° v. UT, ES: 30° n. UT, keine Steuerzeitenverstellung.
2. B) Drosselloser Komfort-Motor aufgeladen, mit Arbeitskammer-Zündfolgenwahl und großer Arbeitskammerzahl, der sich aufgrund seiner geringen Baugröße und kleinem Gewicht, hoher Laufruhe und Effizienz hervorragend auch als Hybrid-Komponente eignet:
   • Diese Strategie verwendet die in [0024]a, b und c beschriebenen Betriebsmöglichkeiten mit elektronischer Zündung.

Under these conditions [...] a ... e different combustion process strategies have to be followed:

1. A) The use as a range extender is due to the precise operation as a battery charger to be designed advantageously for efficiency, effort and pollutants: No ZFW, the regulation for gas exchange ring application is omitted, since this operating mode works with constant combustion chamber pressure. The regulation for oil mist extraction can also be simplified to the reference variables of temperature and quantity, since here too the uniform mode of operation generates usable measurement data from the behavior of temperature and extraction quantities. fuel: Gas 90 Octane, working space: approx. 600 cm ³ , n = 3000rpm, number of chambers 9 , e = 6 mm, compression: 10, without throttling, without charger, P = 25 kW, outer diameter approx. 350 mm, chamber length = 80 mm, total length approx. 200 mm. Weight: approx. 50 kg, ignition with spark plug, λ = 1. Injection in the intake cycle: 45 ° after LOT, internal EGR through AS: 15 ° after LOT, EÖ: 15 ° from LOT, other valve timing: AÖ: 10 ° v. UT, ES: 30 ° UT, no timing adjustment.
2. B) Throttleless comfort engine, charged, with a choice of working chamber firing order and a large number of working chambers, which is also ideal as a hybrid component due to its small size and light weight, smooth running and efficiency:
   • This strategy uses the electronic ignition operating options described in [0024] a, b and c.

As a result of the choice of working chamber firing sequence, ZFW, the number of working chambers to be used per revolution (with 4-stroke operation per 2nd Revolutions) correspond to the load requirement specified. The specified speed, EGR percentage, gas exchange settings {(early or late with the synchronous web adjustment ( 35 )} and air ratio λ depend on the optimum values available through autonomous learning in engine management.

At full load, all existing working chambers are activated with the optimum values with fuel injection per revolution.

The required speed is specified by the engine management based on autonomously learned data at partial load and also at full load. Even at full load, the quality requirements for exhaust gas and efficiency are met.

In the 21 The gas change times mentioned refer to average speeds in the case of spark ignition. The constant overlap angle can remain very small at 20 °, since E-EGR is required for ZFW operation due to the lack of residual gases for exhaust gas optimization. At full load and high speed, the late setting of the load change times gives us the advantage of better filling with delayed intake closing AS. For the internal combustion engine according to the invention, however, the thoroughly premixed combustion, also called the combustion of homogeneous gas-air mixture, is of the greatest advantage. It requires the full use of the intense turbulence in the "effective combustion chamber" (point [0024a]) both during the intake and during the compression stroke. For this purpose, the entire width of the injection pulse is divided into at least two parts.

Here it is important to use the first injection part P1 to start clearly after LOT at approx. 45 ° EW in order to determine the edge volume of the flat work area 3rd ) to be occupied predominantly with residual combustion gas from I and E EGR. This ensures that the homogeneous mixture in the defined combustion chamber ( 8th ) is concentrated and no knockable nests form in the harmful area of the sliding gate environment, namely in the peripheral volume away from the combustion chamber, until the time of ignition.

The moderate increase in geom. Compression to the area around 12: 1 {with e-charger, λ = 1.0 ... 1.2 and inlet opening at 10 ° v. LOT, outlet closing by 10 ° n. LOT, ES at 20 ° a.UT, AÖ at 30 ° a.UT, (all times at medium speeds)} is facilitated by the intense turbulence with regard to the risk of knocking. ( 21 )

The power control or regulation without inlet throttling uses the flexible working chamber ignition sequence selection ZFW in accordance with [0024] b).

On the one hand, this ensures that the optimum operating point is maintained regardless of the power requirement, and that all the existing working chambers are equally loaded. Since the selection of the working chambers is done by switching the fuel injection on and off, all intermediate stages of these multi-chamber engines could in principle also be operated. That means: one or two active combustion chambers are started per revolution. The engine management system selects itself according to the changes in the accelerator pedal position of the Vehicle the number of combustion chamber numbers required due to the load and their even firing order distribution.

I.e. in the case of larger increments between the active number of chambers per cycle kept at the optimum operating point, automatic gear selection or injection quantity and boost pressure variation with optimum λ and / or varied gas exchange times must be used within the most favorable target values.

In order to achieve the pollutant proportions and consumption values required in [0024] c), the combustion of the homogenized fuel-air EGR mixture ensures that the result is low in CO ₂ , NOx and particles at compression-favorable compression pressures. It should be taken into account that the gas turbulence during the compression stroke at a speed of 20 m / s already at n = 3000 rpm when flowing into the effective combustion chamber ( 8th ) is based.

Avoiding soot particles is also an issue under these conditions, with evenly distributed heat generation and a wide range of burning times, e.g. 3 ms on average and burning speeds of 20 m / s ensured in very small combustion chambers.

This also applies to very good consumption values, which are favored by the high compression, medium air ratio, relatively high EGR and intensive premixed combustion.

C) Efficiency motor operated independently of the load in the Homogeneous Charge Combustion Ignition mode (HCCI).

The sum of all described development potentials of the internal combustion engine according to the invention is necessary for this combustion strategy.

Very important compared to the intensive premixing homogenization of the fuel-air EGR mixture {a) + b) in point [0024]} is the basis for the safe HCCI mode of the engine according to the invention, the spreading of the operational safety to the entire performance spectrum by Dissolution of the required performance spectrum in performance levels from different firing sequences of activated working chambers ( 3rd ) [0027]. The engine according to the invention is continuously brought into the optimal, precise map area of the respectively active combustion chambers by control for the exact, quick achievement of the 3-fold goal of performance + exhaust gas quality + consumption.

The use of ferrous materials such as vermicular casting (GJV) for the housing ring ( 2nd ) advances operational safety and efficiency by improving tightness, warm behavior and heat loss. The unfavorable ratio of wall area / working volume of the working chambers ( 3rd ) is compensated for by the low thermal conductivity of the iron materials.

The complete, homogeneously premixed combustion requires, as indicated in [0024] c), the full use of the intensive turbulence in the effective combustion chamber ( 8th ) [Point 0024] even during the intake cycle. The entire injection pulse width thus receives the best possible premix length. It is important to start the fuel injection clearly after TDC at approx. 45 ° KW in order to fill the peripheral volume of the flat work area far from the combustion chamber with residual combustion gas. This ensures that the homogeneous mixture concentrates in the defined combustion chamber and that no knockable nests form in the harmful area of the sliding gate environment, namely in the peripheral volume away from the combustion chamber, until the time of ignition.

The greatest promotion of evenly mastery of self-ignition (of course not only in the HCCI process) causes the absence of overheated edges and surfaces of poppet valves. which are not in the area of the even, large wall surfaces of the eccentric ring ( 1 ) and housing ring ( 2nd ) can be found.

The strong increase in compression to the area around 16: 1, e-booster up 2nd bar, λ = 1.2 ... 1.4 and outlet opening 30 ° v.UT, AS at 20 ° n. LOT, EÖ at LOT, ES at 40 ° a.UT (all times at medium speeds ( 22 ), the safe compression ignition is facilitated by the principle of common advance adjustment and the greater ignition delay caused by the larger I-EGR + E-EGR portion. ( 21 )

Due to the I-EGR components, which are dosed by synchronous gas exchange variation, the regulation for compliance with the auto-ignition time is from 0 ° ... 15 ° n. ZOT possible with the associated heating maximum, so that the combustion takes place in approx. 1.5 ms to approx. 30 ° according to ZOT. The decisive auto-ignition timing as a controlled variable is determined by analyzing the torque curve from the drive of the gas exchange ring ( 9 ) ( 18th ) or by analyzing the seismic signal from the sensor ( 46 ) on the actuator ( 19th ) the application force of the gas exchange ring ( 9 ) where the peak of the heating maximum is clearly above the eccentric shaft angle ° EW of the respective working chamber ( 8th ) is emerging. The torque (torque sensor ( 36 )) for the regulation of the gas exchange ring ( 9 ) is on the stepper motor of the planetary bridge adjustment ( 35 ) to disposal. For the required dynamics of the data processing taking place here, the merging of the signals mentioned is of crucial importance.

The processing of the signals even during ZFW operation is no problem for the engine electronics, since the individual combustion chambers ( 8th ) are activated and monitored.

The Z method of the Finn Aumet Oy mentioned in point [0014] is used as an example for the possibilities of strategy development with the gas exchange ring ( 9 ). The spatial and material conditions of the combustion chamber available with the present invention ( 8th ) offer advantageous applications, for example with the Z process.

With the 2-stroke channels in the gas exchange ring ( 9 ), large overlap EÖ-AS in the push-out cycle, synchronous gas exchange adjustment, throttle-free, electric high-pressure charger, HCCI analysis as described in [0029], the ZFW can not only operate the entire performance spectrum of the engine in HCCI, but also the temperature conditions due to the alternating Active chambers easier to control. These very short and late injection times are matched by the short distances, the high I-EGR temperatures and the intensive squish [0005].

23 shows an example of the gas change times of the Z-process with injection area P2 during compression. P1 is omitted.

The injection of CNG natural gas at the time P2 It also makes it easier to mix the fuel and air mixture.

The gas exchange ring ( 9 ) contributes to the Z process 15 Working chambers in synchronism with the eccentric shaft 15 +1 = 16 programs, the reduction compared to the eccentric shaft ( 7 ) is 15 + 1 => 16: 1 because, due to the eccentric shaft per revolution ( 7 ) Gas exchange ring traveling with 1 program block ( 9 ) just 15 Combustion chambers are fully operated during an eccentric revolution.

The power control or regulation without inlet throttling uses the flexible working chamber ignition sequence selection ZFW in accordance with [0024] b) in the HCCI strategy. On the one hand, this ensures that the optimum operating point is maintained regardless of the power requirement, and yet all existing working 3rd ) evenly stressed. Since the choice of chambers of labor ( 3rd ) by switching the fuel injection on and off, all intermediate stages of these multi-chamber engines could in principle also be operated in the shutdown mode. For reasons of low-noise and low-vibration concentricity, only here, for example 6 Considered levels.

The 25% transitions z. B. between the levels held by control at the optimum operating point must be driven by gearbox selection or injection quantity and boost pressure variation with optimal air ratio λ or varied gas exchange times within the most favorable target values.

For these optimization tasks with the target values CO ₂ , NOx, particles, power and the manipulated variables injection quantities, boost pressure, EGR percentage, air ratio λ and ZFW, the use of control technology with closed control loops is expedient.

Illustrations of the exemplary embodiment

In 23 Drawings, data flow and functional diagrams support the description of the exemplary embodiment: (Data on the exemplary embodiment in [0001], [0005] and [0009])

1 shows in a longitudinal section through the mechanical part of the example motor (picture left) the subdivision into the eccentric housing ( 31 ), formed from the housing ring ( 2nd ) and the two side parts (13g + 13öl). The main camp ( 29 ) as a cylindrical roller bearing carry the eccentric shaft ( 7 ) with a mounted counterweight to accommodate the large eccentric bearing ( 30th ), also a cylindrical roller bearing.

The counterweights needed to compensate for the eccentricity of the eccentric ring ( 1 ) not the entire volume of the eccentric housing ( 31 ).

Over the eccentric ring ( 1 ) the combustion chamber is in the TDC position ( 8th ) with the ignition and injection system ( 11 ) in the housing ring ( 2nd ) and a partial volume in the side part ( 13g ).

In the OT position, the combustion chamber is clearly separated ( 8th ) of the working volume of the working chambers ( 3rd ) in both cuts. Taking into account the thermal expansion, the remaining gap between the eccentric ring ( 1 ) and housing ring ( 2nd ) against 0.1 mm. This is where the high squish speeds from the working chambers ( 3rd ) into the combustion chambers ( 8th ) in:> 20m / s in the embodiment.

The left side of the longitudinal section contains in the gas housing ( 16 ) the storage and the drive of the gas exchange ring ( 9 ), with its channels, the 4-stroke programs for the combustion chambers ( 8th ) executes. This feature comes in with the larger scale 2nd described.

In cross section in 1 on the right is the sequence of the eccentric movement to form the work movement in the working chambers ( 3rd ) vivid: the eccentric ring ( 1 ) forms with the 2 × e larger housing ring ( 2nd ) the crescent-shaped space of the working chambers 3rd with the width of the eccentric ring ( 1 ) and is supported by the 15 Isolating slide ( 4th ) not only in the number of working chambers ( 3rd ) divided, but also against the low torques of the roller bearing friction ( 30th ) against the direction of rotation (eg clockwise). The swivel angle goes from this cross section δ the separating slide ( 4th ) compared to their center position at top dead center OT or bottom dead center UT, which the isolating slide ( 4th ) maximum with their storage, the calottes ( 5 ) in eccentric ring ( 1 ) and housing ring ( 2nd ) until it stops in the spherical cap slot ( 4e ) ( 12th and 13 ) that the movement of the eccentric ring ( 1 ) runs in a circular path with the radius "e" without disturbing vibrations. The number of working chambers ( 3rd ) is not only dependent on the expansion in terms of combustion technology and the optimal adjustment of the eccentric ring ( 1 ) to housing ring ( 2nd ), but also by avoiding disturbing vibrations in the eccentric ring drain.

In the 11 to 16 are details of the swivel angle δ and the functions of gate valves ( 4th ) and domes ( 5 ) illuminated.

At a glance the 1 With 3rd is the function of the oil-gas extraction through the pumping action of the isolating slide ( 4th ) clear. The position of the isolating slide ( 4th ) when covering the oil drains ( 61 ) explains the effect of the separating slide ( 4th ) as an oil delivery valve: open the pressure movement, close the suction movement in cooperation with the flutter valves ( 32 ).

This overview in 1 , 2nd and 7 also shows the different connections: air inlets ( 41 ) in the annulus of the gas exchange ring ( 9 ), Exhaust connections ( 33 ) from the annulus of the gas exchange ring ( 9 ), Labyrinth air ( 23 ), Oil inlet in the gas housing ( 27 ), Oil suction ( 63 ) from gas housing ( 16 ), Oil supply in the oil distributor rings ( 28 ) of the eccentric housing ( 31 ), Oil suction ( 64 ) from the oil annulus ( 26 ) the eccentric side, cooling water inlet in the ring line ( 24th ) in the gas housing ( 16 ), Cooling water return ( 25th ) from the ring line in the side part ( 13 oil ).

2nd highlights the details of the function of the gas exchange ring ( 9 ): The enlargement of the gas housing half ( 16 ) shows how the between the axial ball bearing ( 21 ) and the sliding surface around the combustion chamber opening ( 22 ) guided gas exchange ring with a diameter of 400 mm ( 9 ), is created: from the planetary set ( 15 ) driven by electromagnetic actuators ( 19th ) via the axial ball bearing ( 21 ) and spring-loaded screw connections ( 17th ) connected to the ball-guided (20) flange.

Due to the spring-loaded tapered segments ( 18th ) the gas exchange ring ( 9 ) also centered on thermal expansion.

On the opening of the combustion chamber ( 22 ) opposite surface of the gas exchange ring ( 9 ) the labyrinth sealing rings ( 23 ) with their compressed air supply for the separation of the inlet air ( 41 ) from the exhaust area ( 33 ) visible, which in contact with the gas exchange ring surface the inlet annulus ( 41 ) which surrounds the straight inlet duct inclined to the direction of rotation ( 12th ) the combustion chamber ( 8th ) ventilated ..

The exhaust gas outlet ( 33 ) from the annulus of the gas exchange ring is representative of the required connections of an exhaust manifold, not shown.

The cooling water connection for the ring distributor ( 24th ) with water supply via ring distributors ( 24a ) and ( 24b ) in the side part ( 13g ) via the O-ring seals through the housing ring ( 2nd ) to the cooling water outlet loop ( 25th ) becomes clear here.

On the left end plate of the gas housing ( 16 ) is the schematic gear drive ( 35 ) for the adjustment of the gas exchange ring ( 9 ) via the rotating planetary web ( 34 ) to recognize.

Finally, the sealing elements and oil-gas guides on the eccentric ring ( 1 ) with the position of the sealing segments ( 39 ) and the oil control ring ( 37 ) called, which can also be omitted under the demand for stronger oil production due to the narrow manufacturing tolerances. Likewise here are the oil-gas production elements ( 32 ) and ( 61 ) with the oil mist collecting ring ( 26 ) on which, as well as on the sealing elements, in the 8th , 12th , 13 , 14 and 15 is discussed in more detail.

3rd deals with the functions of the isolating slide group ( 4th ).

The longitudinal section through the bottom dead center UT shows on the right side between the two side parts ( 13g ) and ( 13 oil ) a longitudinal cut through a separating slide ( 4th ). The position of the different parts of the calotte under the separating slide ( 4th ) is shown with a broken line.

The function of the 30 ° inclined division of the isolating slide becomes clear ( 4th ) due to the spring force ( 4d ) the two parts ( 4a) and ( 4b ) presses sealingly against the side surfaces. For this purpose, the isolating slide part ( 4a) with retaining bolts ( 4f ) fixed radially.

The two dome guide lugs ( 4g ) are drilled in the eccentric ring ( 1 ) 1 added to the eccentric housing ( 31 ) through the respective flutter valves ( 32 ) can be closed or opened for the oil-gas flows.

For oil-gas production through the relative movement of the separating slide ( 4th ) → eccentric ring ( 1 ) the mixture drawn in in the drawn position UT when the valve closes ( 32 ), which is caused by the movement of the eccentric ring ( 1 ) is accelerated positively by the opening oil drains ( 61 ) via the ring line ( 26 ) in the oil suction ( 64 ) stream.

In 11 to 15 details of the isolating slide group are deepened.

The arrangement of the oil-gas extraction ( 63 ) from the gas housing ( 16 ) over the gas exchange ring ( 9 ) corresponds to the optimal position for flushing and cooling the gas housing ( 16 ). The inevitable guidance of the oil mist through the axial bearing ( 21 ) and through the openings (dashed) of the gas exchange ring flange is for cooling the gas exchange ring ( 9 ) optimal. Thorough extraction at the lowest point of the extractable gas housing space ( 16 ) is for checking the sliding conditions of the gas exchange ring ( 9 ) of great importance.

7 illustrated on the right-hand side with a cross section of the gas housing ( 16 ) both the arrangement of the planetary drive ( 15 ) for the gas exchange ring ( 9 ) and the elements for guiding the gas exchange ring ( 9 ) as well as the course of the cooling water channels for the thermally important combustion chamber cooling ( 24th ), ( 24a ) u. ( 24b ) and various other connection distributions on the gas housing side ( 16 ).

The planetary drive ( 15 ) forms with the storage of the reduction wheels in the web ( 34 ) via the stepper motor drive ( 35 ) the gas change times can be adjusted by the stroke length shown by two cycles, ie 360 ° EW. The triple set of the planetary gear ( 15 ) distributes the driving forces to the large internal ring gear of the gas exchange ring ( 9 ) even, causes exemplary oil distribution and oil mist formation with the oil supply ( 27 ) centrally in the interior of the planet web ( 34 ) with a reduction ratio of 1:16. The air supplied occasionally via the ventilation valve ( 55 ) brings additional swirling and cooling into the highly stressed gas housing ( 16 ).

The elements of the gas exchange ring guide with eight evenly distributed electromagnetic actuators ( 19th ) and the corresponding number of tapered segments ( 18th ) to compensate for the radial thermal movements of the gas exchange ring ( 9 ) are in the upper 120 ° part of the cross-section between the arc of the combustion chambers ( 8th ) - gas channels 12th - arrangement and the planetary drive ( 15 ) highlighted.

The lower right third of the cross-section shows the conductor structure (broken line) of the cooling water flow with the ring lines ( 24a , b) and the surrounding combustion chambers ( 8th ) in the side part ( 13g ).

Several cooling water connections to the ring conductor ( 24th ) for water inlet, tends to be below, and the return flows from the ring main ( 25th ), tending to be at the top, have an influence on the cross flow around the combustion chambers due to the diagonal position ( 8th ) within the ladder structure in the side part ( 13g ).

In 5 are the forces on the eccentric ring with a schematic representation ( 1 ) as a force vector of the sum of the attacking gas forces of the individual expanding working chambers ( 3rd ) summarized, which with its strength in the direction through the center of the eccentric ring ( 1 ) and the lever = e × cos α gives the drive torque of the machine.

6 represents the schematic roller guide of the eccentric ring ( 1 ): especially in the sectional view B - B it becomes clear how the eccentric ring ( 1 ) with the selected dimensioning on the leading role ( 62a ) with all mass points on the circle with the diameter 2 × e.

8th shows with an enlarged drawing (about 1: 2 to reality) the importance of the cooling water flow of the ring line ( 24th ) about the ladder structure ( 24a-24b ) there.

The location of the seismic sensor ( 46 ) on the encapsulation of the magnetic actuator ( 19th ) can be seen here.

The guidance of the rotating planetary web ( 34 ) in gas housing ( 16 ) and side part ( 13g ) and the convenient position of the oil supply ( 27 ) are clearly visible.

The oil mist guide in the eccentric housing ( 31 ) with the inputs via the oil distributor rings ( 28 ) in the side parts ( 13g ) u, ( 13 oil ) and onward transport via the main warehouse ( 29 ), swirled radially by the eccentric shaft ( 7 ) partially across the eccentric bearing ( 30th ) due to asymmetrical suction to the oil mist collector ( 26 ), accelerated by the pumping action of the isolating slide ( 4th ) via the flutter valves ( 32 ) is illustrated here. Details of the coil tape springs ( 14 ), which the combustion chamber openings ( 22 ) against the gas exchange ring ( 9 ) seal, are in 10th treated.

9 shows a cross section through the gas housing ( 16 ) at the level of the planet gears, in the background with a partly broken line a part of the gas exchange ring ( 9 ) and provides information about the processes on the gas exchange ring ( 9 ) with its channels for ventilation of the selected in the example 15 Combustion chambers ( 8th ).

For the gas exchange ring ( 9 ) the number of 4-stroke programs to be included and the reduction ratio for the drive must be determined.

• Die Exzenterwelle (7) muss bei 2 Umläufen, relativ zum sich mitdrehenden Gaswechselring (9) 15 mal 4-Taktprogramme durchlaufen. Bei 2 Umläufen ist der Gaswechselring aber relativ zur Exzenterwelle (7) und den Brennräumen (8) um ein 4-Taktprogramm weitergelaufen. D.h. durch den Gleichlauf werden nur (2 × Anzahl der Programme auf dem Gaswechselring) - 1 = 15 Programme durchlaufen, daraus folgt für die Anzahl der 4-Taktprogramme = (15+1)/2 = 8 Programmsätze auf dem Gaswechselring (9).

As with the 4-stroke sequence 2nd Eccentric revolutions, regardless of the starting point, the exact same state for the position of the gas exchange ring ( 9 ) must be restored to the combustion chambers and each combustion chamber ( 8th ) must be operated once by the complete 4-stroke program, results, for example, when the eccentric shaft is synchronized ( 7 ) and gas exchange ring ( 9 ) the requirement:

• The eccentric shaft ( 7 ) must be 2nd Revolutions, relative to the rotating gas exchange ring ( 9 ) 15 run through 4-stroke programs. At 2nd The gas exchange ring is circulating relative to the eccentric shaft ( 7 ) and the combustion chambers ( 8th ) continued with a 4-stroke program. This means that the synchronization runs only (2 × number of programs on the gas exchange ring) - 1 = 15 programs, which means for the number of 4-cycle programs = (15 + 1) / 2 = 8 program blocks on the gas exchange ring ( 9 ).

The following applies to the reduction ratio in the exemplary embodiment: 2 × rotation d. Eccentric shaft per 1/8 turn of the gas exchange ring or 16 turns d. Eccentric shaft for 1 revolution of the gas exchange ring = 16: 1 reduction ratio of the eccentric shaft ( 7 ) to gas exchange ring ( 9 ).

The opposite direction of rotation results under the same conditions (now due to the opposite direction with an additional program run): Number of programs = (15-1) / 2 = 7, and speed eccentric shaft / gas exchange ring = (15-1) / 1 = 14: 1.

• Im OT beim I. Brennraum (8) beginnt der Expansionstakt, der vorhergehende Brennraum XV. steht voll im Ladungswechsel beim Einlasstakt (12), der Brennraum II. befindet sich nach Auslass (65) nun im beginnenden Einlass (12), ohne Überschneidung und Brennraum III. steht in der Endphase der Kompression.

About ¼ of the gas exchange ring, corresponding to 2 × 4 cycle programs, are in 9 highlighted:

• In the OT at the 1st combustion chamber ( 8th ) the expansion stroke begins, the previous combustion chamber XV. is fully in charge change during the intake stroke ( 12th ), the combustion chamber II is after the outlet ( 65 ) now in the beginning entrance ( 12th ), without overlap and combustion chamber III. is in the final phase of compression.

The positions of the actuators ( 19th ) are drawn in for the gas exchange ring and there are the same number of tapered segments ( 18th ) for centering the gas exchange ring ( 9 ) under their tension ring ( 66 ).

For feeding the oil-gas mixture into the oil distributor ring ( 28 ) of the side part ( 13g ) as well as for the adjustment drive of the planetary web ( 35 ) the space between the planetary gear sets outside the planetary web ( 34 ) utilized.

10th represents greatly enlarged (thickness of the side part ( 13g )) the longitudinal section of the combustion chamber construction with the details: sliding surface of the gas exchange ring ( 9 ), Combustion chamber opening ( 22 ), Combustion chamber ( 8th ) in the side part ( 13g ), Incision ( 10th ) in the housing ring ( 2nd ) and the top in TDC of the eccentric ring ( 1 ).

The representation of the spiral ribbon spring ( 14 ) shows the setting of the individual windings in a pretensioned manner, whereby the middle bands, as the side view shows, produce the resilient function and the tightness in the offset area by overlapping transitions. The function can be adjusted by the number of turns, in particular for the tightness and dimensioning of the spring stiffness or the natural frequency and in accordance with the loads.

The construction of the spiral band spring ( 14 ), however, is very intensive against vibrations and tendency to resonate due to the strong friction damping between the windings lying together under load, with stimulating sliding contact with the gas exchange ring ( 9 ), equipped.

The cooling water distribution rings ( 24a ) and ( 24b ) complete the illustration and the complex sealing segment ( 39 ), the gas tightness in the eccentric ring ( 1 ) between the domes ( 5 ) the isolating slide ( 4th ) resilient, is in the 13 , 14 and 15 treated in detail.

The shape of the combustion chamber shows an undisturbed simplicity, which is not impaired in its effect as an effective combustion chamber, even by the ignition and injection units that are only indicated.

For superior effectiveness of the squish function with 95% of the working chamber volume, which is already in the combustion chamber at medium speeds of over 20 m / s ( 8th ) should not be kept silent when looking at this construction.

11 shows enlarged the composition of the separating slide calotte system in cross section at the OT.

The lead ( 4c ) guides the oil-gas mixture with its longitudinal groove from the sliding gate sealing surfaces to the suction openings ( 61 ).

The sealing segments ( 39 ) form with the calottes ( 5 ) of the eccentric ring ( 1 ) a springy chain.

The division of the domes ( 5 ) with their holes for the contact springs ( 5c ) leads to the tightness of the entire system. ( 12th )

The center distance of the calottes ( 5 ) in TDC, k1 + k2, determines half the swivel angle with the eccentricity e δ the separating slide ( 4th ).

The short retaining bolts ( 4f ) in its recess in a slide valve ( 4a ) and dome edge on the gas housing side ( 2nd ) become clear.

The valve function of the by eccentric ring ( 1 ) - or the separating slide ( 4th ) - Movements connected oil-gas openings ( 61 ) in eccentric ring ( 1 ) and housing ring ( 2nd ) is explained. In the lower left corner you can see that the oil openings ( 61 ) through the eccentric ring movement also the relief holes ( 62 ) approach. ( 11 )

• Gegenseitige Führungen durch die Scharnierwirkung der Kalottensätze (5a - 5b), durch die Führungsnasen (4g) des Trennschieberteils (4a) und durch die Haltebolzen (4f) auf der Gehäuseringseite (2).

In 12th you can see how sliding gate valves ( 4th ) and domes ( 5 ) work together. The longitudinal section on the right half shows the position of the dome parts ( 5a , 5b ) under the slide valve ( 4th ) indicated by broken lines:

• Mutual guides through the hinge effect of the calotte sets ( 5a - 5b ), through the guide lugs ( 4g ) of the separating slide part ( 4a ) and through the retaining bolts ( 4f ) on the housing ring side ( 2nd ).

Mutual seals against eccentric ring ( 1 ), Housing ring ( 2nd ), Side parts (13g + 13öL) and sealing segment sets ( 39 ). The mutual sealing is characterized by the inclined division of the separating slide ( 4a ) and ( 4b ), which by means of spring pressure ( 4d ) the side parts ( 13 ) contacted. The contact with the side parts 13 also effect the calotte quarters, which are divided by resilient 5c ) in long and short domes ( 5a ) u. ( 5b ) issue. The in the divisions ( 5c ) resulting gaps are due to the mutual alignment according to the position of the guide lugs ( 4g ) covered each other. (see 12th right half, longitudinal section)

The radial preload with the springs ( 5d) serves the safe layout of the Kalottenviertel ( 5a ) and ( 5b ) in the holes of the eccentric ring ( 1 ). ( 12th , 13 u . 14 )

The sealing segment sets ( 39 ) lie in the calottes ( 5 ) with their customized profile.

At the pumping action for the oil-gas production of the eccentric ring movement ( 1 ) against the isolating slide ( 4th ) are next to the oil-gas openings ( 61 ) the flutter valves ( 32 ) in the holes of the eccentric ring ( 1 ) involved.

For lubricating the sliding surfaces on the side parts ( 13 ) and the calottes ( 5 ) on the housing ring side ( 2nd ) promote the grooves in the end faces of the separating slide ( 4a ) and ( 4b ) and in the diagonal division of the separating slide ( 4th ) a partial flow of the oil-gas mixture via the lead ( 4c ) to the openings ( 61 ). The radial preload with the springs ( 5d) serves the safe layout of the calotte quarters ( 5a ) and ( 5b ) in the holes of the eccentric ring ( 1 ).

In 13 with a look at the side surface of the eccentric ring 1 the arrangement and effect of the sealing segments ( 39 ) clear.

The separating slide ( 4th ) have in the drawn position of ° EW = 290 ° +/- 10 °, according to the expansion cycle or with the reverse pivoting of the separating slide ( 4th ) the maximum deflection in the intake cycle at ° EW = 80 ° δ _k and lie in the dome slot ( 4e ) on.

With the 2-part sealing segment ( 39 ) lies on the working chamber side (39a), corresponding to the intermediate spring ( 39c ), in the direction of the eccentric shaft rotation at the calotte ( 5a ) which, due to the anti-clockwise rotation of the isolating slide ( 4th ) here sealing segments under combustion pressure ( 39a ) runs cheaper.

The open gaps between the relieved segment ends and the calottes ( 5a ), ( 5b ) not only guide the gas pressure to the segment ends, but also have to be sealed off at the bottom of the groove: 14 .

14 shows the resilient C-profile spring with cuts A -B and CD ( 39d ), the task of resilient locking ( 39e ) the fission gases takes over and at the same time the resilient, axial application of the sealing segments ( 39a ), (39b) against the side parts ( 13 ) causes.

15 clearly shows with the section A -A the subtleties of the sealing segments ( 39 ) with their components such as the spring-related punctures ( 39e ).

The isolating slide section ( 4th ) is in the contact position to the eccentric ring ( 1 ) mapped.

In 16 runs the δ function ( 6 ) over the rotation of the eccentric shaft ( 7 ) calculated in ° EW = 0 ° at OT.

The function has its maximum in the example at ° EW = 79.2 ° with δ _k = 10.8 ° after the 1st derivative of tanδ: tan'δ = 0 → cos ° EW = 1 / [1 + (k1 + k2 / e)].

Ie the larger the center distance of the calottes ( 5 ) is selected with the same e, the closer the maximum of the swivel angle moves to ° EW = 90 ° and the smaller the swivel angle δ _k . Of the 2nd . Semicircle runs symmetrically to the 1st

17th provides the closed control loop for the dynamic optimization of the sealing contact between the gas exchange ring ( 9 ) and side part ( 13g ) with the spiral band springs ( 14 ) schematically.

The engine management software ( 54 ) and the electromagnetic actuator ( 19th ) are the crucial elements in this important control loop, whose operating data provide very precise information about the qualitative status of the gas exchange ring contact ( 9k ) such as wear, heat distortion and energy consumption, which are used for the learning effects of the software.

18th shows the schematic example of a torque curve and the underlying column and forces between the gas exchange ring ( 9 ) and side part ( 13g ) depending on different operating conditions. (Details in [0017])

19th : The symmetrical, circular arrangement of all essential elements of the internal combustion engine according to the invention does not allow a sensible oil pan located inside the engine housing or the gas housing.

For the two lubrication areas gas housing ( 16 ) and eccentric housing ( 31 ) in the dry sump process, the parallel connection of the two oil circuits is only possible with a suction pump ( 45 ), the oil pressure pump ( 42 ) (which is eliminated with the use of the separating slide pump effect) and the variable oil distributor ( 43 ) provided. To extract the eccentric side ( 31 ) independently, the gas housing ( 16 ) emptied by the internal gas pressure.

With the signals such as temperatures, flow rates and pressures from the two areas and the settling tank ( 44 ) is carried out in cooperation with the control unit ( 54 ) the closed regulation ensured.

20 shows with the series connection of the two lubrication areas the effective use of the isolating slide pump for suctioning the eccentric side ( 31 ), very effectively supported by the suction pump ( 45 ), which creates the overpressure in the settling tank and the underpressures in the two housings ( 16 ) and ( 31 ) connected to the ventilation valve ( 55 ) regulates.

The excess pressure in the settling tank doses the oil supply ( 27 ) to the gas housing ( 16 ).

With the signals such as temperatures, flow rates and pressures from the two areas and the settling tank ( 44 ) is carried out in cooperation with the control unit ( 54 ) the closed regulation ensured.

21 shows the gas exchange times of the three described combustion strategies, divided into work and charge groups.

The settings are not extremely designed to accommodate the adjustments due to synchronous time shifts that occur with the web adjustment ( 34 ) run very dynamically to give enough space. Extreme adjustments are made with the valveless combustion chamber ( 8th ) executed without any problems with each overlap. Very early inlet closing is compensated for by the electric charger as needed.

A comparison of the effectiveness of reciprocating piston engines with valve disks and jagged piston heads designed combustion chambers leads, despite extremely complicated valve controls, to the conclusion that without an effective combustion chamber with an optimal size and shape, there can be no harmonious result regarding the challenges of efficiency and exhaust gas quality.

22 lists the control values of strategies A, B u. C including injection times and spark ignition.

Comments have been added on effects and compensation options.

In procedure C, the injection concentrates on P1 during the intake cycle in order to provide a period of stabilization as long as possible with significantly reduced P2 with approximately 300 ° eccentric angle → 17 ms at n = 3000 rpm for the homogenization.

After this time, the gas charge with high real compression (geometric + boost pressure) is still in full residual squish of about 1 mm eccentric ring travel with gas speeds> 20 m / s and about 1 ms duration at n = 3000 rpm. If during this period, at 5 ° v. ZOT the self-ignition does not occur yet, is spark-ignited with spark plug. Operation with CNG natural gas ensures the homogenization of the fuel-gas-air mixture and improves ignition stability thanks to its gas properties.

For this HCCI process, the engine management has a sector "auto-ignition search program", which consists of the "pressure-lambda-temperature-seismic sensor pulse ( 46 ) “- Data situation readjusted, for example, with the change in pressure of the electric charger.

SI spark ignition helps to operate the machine without malfunction. The aforementioned data development enables the electronic control system to automatically improve its own program.

23 describes the 2-stroke gas exchange of the so-called Z process, implemented according to the present invention.

It was originally practically a 2-stroke engine with poppet valves in the combustion chamber, the pressure level of which is generated outside the crankcase for the gas exchange. Here, too, the engine according to the invention has the advantage of a combustion chamber without a valve disk.

Despite the very late inlet closing at 90 ° EW UT, there is still a 90 ° EW compression angle: with the possible charging to at least 0.2 MPa, this corresponds approximately to a naturally aspirated engine filling.

There is an HCCI option. List of reference numbers Internal combustion engine AZ 10 2018 007 650.5 1 reference meaning Remarks (1) Eccentric ring drives the eccentric shaft (7) via bearings (30) (2) Housing ring. Inner radius = R forms with the side parts (13g), (13öl) the eccentric housing (31) for (1) and (7) (3) Working chambers Expansion space in the interior between (2) and (1). Eccentric chamber (3a) (4) Isolating slide Main (4a). Secondary slide (4b). Lead (4c) Leaf spring (4d). Calotte slot (4e), retaining bolts (4f), guide lugs (4g) (5) Quartered domes Quarter calottes long (5a) u. short (5b) cross-divided for spring mounting (5c). Preload (5d), tasks: guiding and sealing the separating slide (4) to the eccentric ring (1), side parts (13g). (13 oil) and sealing segments (39) (6) Contact angle δk δk = half max. Swing angle of the separating slide (4) (7) Eccentric shaft (8th) Combustion chamber Space outside the eccentric chambers (3) at OT (9) Gas exchange ring Contact sliding surface (9k) (10) incision Part of the combustion chamber (11) Injector, spark plug (12) Inlet duct forms the gas exchange program in the gas exchange ring (9) with the outlet duct (65) (13) Side panels Gas side (13g). Clutch side (13oil) (14) Coil spring Sealing element between the combustion chamber (8). Combustion chamber opening (22) and gas exchange ring (9) (15) Planetary gear drive 3 planetary gear sets for driving the gas exchange ring (9) (16) Gas housing Housing of the gas exchange side (17) Internally toothed ring gear of the planetary gear carries the driver tongues (18) for driving the gas exchange ring (9) (18) Driver tongues on the ring gear (17) Centering and driving the gas exchange ring (9) with 12 axially parallel driver tongues (18) (19) Actuator, preload (19a) Electro-magnetic gas exchange ring application on bearing (21) (20) omitted (21) Axial ball bearing (22) Combustion chamber opening between gas exchange ring (9) and combustion chambers (8) (23) Labyrinth sealing rings with compressed air supply between gas housing (16) and gas exchange ring (9) (24) Ring line cooling water on in gas housing (16) Ring distributor (24a) u. (24b) in the side part (13g) as a ring conductor for cooling the combustion chambers (8) (25) Ring line cooling water off integrated in the side part (13 oil) (26) Ring line oil mist collector integrated in the side part (13 oil) (27) Oil supply gas side (28) Oil distributor ring eccentric side in the side part (13g) + (13öl) (29) Eccentric shaft main bearing (7) Cylindrical roller bearings (30) Eccentric bearing Cylindrical roller bearings (31) Eccentric housing (32) Check valves in (1) 3 ring segments (32a) / side with 5 flap valves each (33) Exhaust gas routing in the gas housing (16) from the annulus of the gas exchange ring (9) (34) Planet footbridge Adjustment of gas change times (35) Bridge control time adjustment Stepper motor drive (36) Torque sensor for driving torque of the gas exchange ring (9) (37) Roof chamfer ring in the eccentric ring (1) on the oil chamber side (38) Steel spring washer C- cross section in the housing ring (2) (39) Sealing segment. two parts in the eccentric ring (1) with individual parts. between eccentric ring (1) and side parts (13). Combustion chamber side: (39a). inside: (39b). Intermediate spring: (39c). C-profile spring: (39d), spring-related recesses: (39e) for permanent sealing tension between the calottes (5) (40) Oil groove in the separating slide bevels and sealing surfaces (41) Inlet annulus Inlet distributor integrated i. Gas exchange ring (9) (42) Oil pressure pump Dry sump process in parallel (43) Oil distributor Dry sump process parallel u. serial (44) Settling tank Dry sump process parallel u. serial (45) Suction pump Dry sump process parallel u. serial (46) Seismic signal transmitter on the electro-magnetic actuator (19) (47) Oil valve Dry sump process parallel u. serial (48) Oil filter Dry sump process parallel u. serial (49) oil cooler Dry sump process parallel u. serial (50) Pressure and flow sensor Negative pressure in the gas housing and eccentric housing (51) Temperature sensor Gas housing side, gas exchange side (52) Temperature sensor Eccentric side (53) Flow meter Quantity of oil-gas from eccentric space (31) (54) Control device in engine management (55) Ventilation valve for gas housings (16) (56) Gas valve on the settling tank Blowby u. Control air return to gas inlet (57) Pressure sensor Pressure in the settling tank (44) for oil metering (58) Flow meter for analyzing the gas ratios (59) Temperature sensor (60) Pressure sensor Vacuum eccentric side (61) Oil drains controlled by a slide valve (4) (62) Relief and guide holes Aspirated via oil drains (61). 62a leadership role (63) Oil-gas extraction Suction from gas housing (16) (64) Oil-gas extraction Suction from ring line (26) (eccentric side) (65) Exhaust duct (66) Clamping ring, not applicable omitted ZFW Working chamber firing order selection Load-dependent selection of the working chambers through ignition sequence variation with the participation of all working chambers, flexible switching off and switching on of the working chamber EGR Exhaust gas recirculation I-EGR: internal. E-EGR: external HCCI Homogeneous Charge Combustion Ignition Compression ignition of homogeneous gas mixtures ° EW Eccentric angle in ° EW Corresponds to ° KW crank angle b. Reciprocating engine R Inner radius from the housing ring (2) e eccentricity Radius of the circular movement of the eccentric ring (1) k1 + k2 Center-to-center spacing smallest distance between the calotte centers in OT, 3a δ Delta in ° half swivel angle of the separating slide (4) λ Lambda Air / fuel ratio ms Milliseconds MPa pressure 1 megapascal = 1 N / mm ² → 10 bar L / s Liters per second Oil-gas mixture quantities per time P1 Part-Inject 1 Fuel injection in the intake cycle P2 Part-Inject 2 Fuel injection in compression cycle SI Spark Ignition electronic spark ignition OT Top Dead Center Gas change or compression maximum at 4 stroke LOT Charge change OT ZOT Ignition OT Subtitles Bottom dead center End of expansion or suction at 4-stroke EÖ Entry in ° EW IT Entry deadline in ° EW AÖ Outlet opening in ° EW AS Outlet cut off in ° EW

Claims (47)

The internal combustion engine with intermittent combustion of the fuel-air mixture contains a housing ring (2) which forms the eccentric housing (31) with an inner diameter of 2 x R with two side parts (13g) and (13öl). The rotatable eccentric shaft (7) with the eccentricity e is mounted centrally in this housing, characterized in that - a large number of combustion chambers (8) are arranged in a circle in its side part (13g), that - their assigned number of working chambers (3) a circular eccentric ring (1) with the outer diameter (2 x R) - (2 xe) in the larger housing ring (2) forms from the eccentric chamber space (3a) that - all the mass points of the eccentric ring (1) are due to its eccentric bearing on the eccentric shaft (7) and the additional separating slide (4) in the eccentric chamber space (3a) on the circular path with the diameter 2 xe that - the eccentric chamber space (3a) through the evenly between the housing ring (2) and eccentric ring (1) radially arranged, pivotable and displaceable separating slide (4) is divided into working chambers (3) that - the gas pressure of the combustion chambers (8) via the working chambers (3) and the eccentric ring (1) on the eccentric Acting, the drive torque of the eccentric shaft (7) produces that - the pivoting and displaceable guidance of the isolating slide (4) in the housing ring (2) and in the eccentric ring (1) takes place in multiply divided cylindrical caps (5) that - the The separating slide (4) can only be moved in the eccentric ring (1) so that - the separating slides (4) lie gas-tight against both side parts (13g) and (13öl), that - the calotte sets (5a) and (5b) opposite the separating slide (4) , Eccentric ring (1), side part (13g) and side part (13öl) work gas-tight and that - for the gas exchange of any number of combustion chambers (8) at least one rotatably mounted, sealed gas exchange ring (9) equipped with the combustion program channels and sealing surfaces from Gas housing (16) ventilated from the combustion chambers (8). (Scheme and 1 , 2nd , 3rd , 4th , 5 ) Internal combustion engine after Claim 1 , characterized in that - the low-vibration guidance of the eccentric ring (1) in a gyroscopic movement around the center of the housing ring (2) with the eccentricity e of the eccentric shaft (7) by limiting the pivoting angle δ (6) of the isolating slide (4) to the decisive maximum angle δk is established that - the division of the eccentric chamber space (3a) is made with at least 7 separating slides (4) evenly distributed between the housing ring (2) and eccentric ring (1) and that - the eccentricity e and the center-to-center distances of the spherical caps k1 and k2 calculated value for δk of the separating slide (4) is used. ( 11 u . 13 ) Internal combustion engine after Claim 1 , characterized in that the low-vibration guidance of the eccentric ring (1) is produced with at least 7 separating slides (4) in that a main separating slider in the eccentric ring (1) is not pivoted, that is only slidably mounted without spherical caps (5). Internal combustion engine after Claim 1 , characterized in that a vibration-free guidance of the eccentric ring (1) with at least 3 guide rollers (62a) arranged evenly either in the eccentric ring (1) or in the side parts (13) is produced by distributing at least 3 evenly on the guide rollers (62a) Roll the guide holes (62) of the eccentric ring (1) with their center on a circle with a diameter = 2 xe without play. ( 6 ), ( 1 ) Internal combustion engine according to the Claims 2 and 4th , characterized in that - the combination of the two guide systems ensures vibration-free, gyroscopic and low-wear guidance of the eccentric ring (1) by the use of the contact angle δk (6) of the separating slide (4) in the spherical cap slot (4e) and the play-free rolling of the guide bores ( 62) on the guide rollers (62a) that - with low bending stiffness of resilient slide valves (4) and up to 10% reduction in the calotte slot (4e) calculated according to e and k1 + k2 and that - working with at least 5 slide valves (4). (6), (11), (13) Internal combustion engine according to one or more of the preceding claims, characterized in that - the pivotable and radially displaceable mounting of the separating slide (4) in the housing ring (2) and in the eccentric ring (1) by means of four asymmetrically cross-divided calotte sets (5a) and (5b) circular cross-section that - the calotte sets (5a) and (5b) each have a compression spring (5c) in their transverse divisions. ( 12th ) and that - the calotte quarters (5a) and (5b) are each radially preloaded in their longitudinal divisions with at least one spring (5d). ( 12th , 13 and 14 ) Calotte sets (5a) and (5b) after Claim 6 , characterized in that - the gaps of the transverse division are alternately aligned with the guide lugs (4g) of the separating slides (4a) and that - the calotte sets (5a) of the outer separating slide guide in the housing ring (2) have a cutout on the inner edges of the catotte quarters Have the holding bolts (4f). ( 12th ) Internal combustion engine according to one or more of the preceding claims, characterized in that the effective combustion chamber (8) is separated from the rest of the eccentric chamber space (3) by minimizing the distance between the eccentric ring (1) and the housing ring (2) and that - during the combustion process of the premixed fuel-EGR-air mixture the distance between eccentric ring (1) and housing ring (2) opens a maximum of 8% of (2 xe). ( 10th ) Internal combustion engine according to claim (8), characterized in that - the transition from the combustion chamber (8) to the eccentric chamber space (3) takes place via at least one incision (10) in the housing ring (2) and / or in the eccentric ring (1), that - the injection - and ignition devices (11) are used in the incision (10) and that - the cross-sectional area of the incision (10) in relation to the cross-sectional area of the combustion chamber (8) is approximately 1: 1. ( 2nd , 10th ) Combustion chamber (8) after Claim 9 , characterized in that - the notch (10) is inclined to the direction of rotation of the eccentric shaft (7) and / or that - the notch (10) is provided with a helical pull and that - the inlet channel (12) in the gas exchange ring (9) is one Tilt against the direction of rotation of the eccentric shaft (7). ( 9 ) Internal combustion engine after Claim 1 , characterized in that - the rotatably mounted and sealed gas exchange ring (9) in a separate gas housing (16) on the side part (13g), contact sliding surface (9a), glides gas-tight and that - the combustion chambers (8) through the channel and Surface elements of the rotating gas exchange ring (9) are ventilated by means of at least one combustion chamber opening (22). ( 4th ) Internal combustion engine after Claim 11 , characterized in that at least one planetary gear set (15) is used to drive the gas exchange ring (9). Internal combustion engine according to the Claims 11 and 12th , characterized in that all the gas exchange elements are arranged on the gas exchange ring (9), the planetary gear sets (15) of which for the adjustment (35) of the gas exchange times are mounted on a planetary web (34) which can be rotated about the engine center. ( 9 ) Internal combustion engine after Claim 11 , characterized in that the gas exchange ring (9) is driven by at least one digitally controlled stepper motor with a flexible program, which also takes over the variations in the gas exchange times. Internal combustion engine after Claim 12 , characterized in that - a stepping motor (35) is used to drive the planetary web (34) and - the stepper motor (35) carries the sensor (36) for the drive torque of the gas exchange ring (9) on its drive shaft. ( 8th ) Internal combustion engine after Claim 1 , characterized in that the housing ring (2) is sealed against both side parts (13g + oil) by steel spring washers (38) with a C cross-section in grooves in the housing ring surfaces, lying outside the combustion chambers (8) and the calottes (5). ( 12th ) Internal combustion engine after Claim 1 , characterized in that - sealing sets (39) between the eccentric ring (1) and side parts (13g + 13oil) each consist of 2 sealing segments (39a) and (39b), which in the eccentric ring (1) per recess parallel between the calottes (5) are inserted that - sealing segments (39a) and (39b) are tangentially braced against each other by an intermediate spring (39c) that - in the form-fitting sealing contact surface of the sealing segments (39a) and (39b) with the domes (5) a defined contact pressure is achieved is that - the combustion chamber-side sealing segment (39a) in the direction of the eccentric shaft rotation ( 13 ) is present that - a recess-wide, steel C-profile spring (39d) creates the axial preload of both sealing segments (39a) and (39b) for the sealing contact to the side parts (13g + oil) that - the C-profile spring (39d) in Eccentric ring (1) between the spherical caps (5), inserted tangentially in the groove base under the sealing segments, that - both ends of these C-profile springs (39d) are positively adjusted in the spherical cap contact - that - due to the spring force of the incised middle part of the C- Profile spring (39d) the circular arc-shaped spring ends form-fit the spherical contact under all operating conditions in a defined manner that - the sealing segments (39a + 39b) lie flat on the flat side of the C-profile spring (39d) that - due to the tolerance-related gap between the combustion chamber-side sealing segment ( 39a) and the puncture wall of the eccentric ring (1) and the pulsing punctures (39e) in the middle part of the C-spring (39d) de Combustion chamber gas pressure in the duct under the C-spring acts to reinforce the sealing contact between the sealing segments (39) and the side parts (13) so that - due to the pressure difference generated between the two outer flanks of the C-profile spring (39d), full contact of the Flank to the eccentric housing-side puncture wall of the eccentric ring (1) is produced, which seals the spring-related punctures (39e) against gas leakage into the eccentric housing (31). ( 11 to 15 ) Internal combustion engine after Claim 17 with sealing segments (39a) u. (39b), characterized in that the sealing contact surfaces to the side parts (13g) + (13öl) are profiled by punctures. ( 14 , 15 ) Internal combustion engine after Claim 1 , characterized in that - the separating slides (4) are divided diagonally into the main slider (4a) and secondary slider (4b), that - both separating slides (4a and 4b) by axially moving the secondary slider (4b) the required sealing pressure on the sliding surfaces of the side parts Generate (13g) and (13öl) and that - the spring pressure (4d) maintains the sealing pressure during operation and allows the necessary return movement when the load is released. Internal combustion engine after Claim 19 , characterized in that - the inclined dividing surface and / or the side part sealing contact surfaces of the separating slides (4a and 4b) are grooved, - that the grooved spring guide (4c) is inserted at the outer end of the main slider (4a) on the housing ring to receive the leaf spring (4d ) and to divert the oil-gas flow to the oil drains (61). ( 12th ) Internal combustion engine after Claims 1 , 11 and 12th , characterized in that - the gas exchange ring (9) is guided at least by an axial ball bearing (21) on the outside of the internally toothed wheel of the planetary gear drive (15) and that - the required basic loading of the axial bearing (21) is ensured by the preload (19a) that - the pre-tensioning (19a) causes the coil springs (14) to be maximally tensioned and - the pre-tensioning (19a) causes the contact sliding surface (9k), which contains the elements of the gas exchange programs, to slide on the side part (starting with the engine) 13g) is generated at flat contact pressure. Internal combustion engine according to one or more of the preceding claims, characterized in that - on the gas exchange ring GWR (9) with two axial labyrinth sealing rings with compressed air supply (23) in the gas housing (16) the exhaust gas (33) and inlet space (12) are separated from each other and that - the two labyrinth sealing rings (23) form an annular space for the Limit inlet gases (12) in the gas exchange ring (9), which is axially opposite the contact sliding surface (9k). Internal combustion engine according to one or more of the preceding claims, characterized in that - the gas exchange ring (9) on the ball-bearing drive wheel (15) is centered with a plurality of spring-loaded screw connections (17) which are uniformly distributed over the circumference and are each carried there by correspondingly radially guided balls (20) is and that - the centering of the gas exchange ring (9) by means of conical segments (18), which are resiliently inserted on the circumference of the drive wheel (15), tracks the thermal expansion of the gas exchange ring (9). ( 4th , 9 ) Internal combustion engine according to one or more of the preceding claims, characterized in that - for sealing the gas transfer between the channels of the gas exchange ring (9) and the openings (22) of the combustion chambers (8), the system-controlled contact pressure of the engine management system (54) serves that - the dimension and dynamics of the electro-magnetic actuators (19), the regulation of the contact pressure in every operating situation ensures that - additionally resilient spiral band springs (14), surrounding the combustion chamber openings (22), work under pretension (19a) so that - the supercharger pressure in the annulus (41) of the inlet (12) when building up the application forces of the gas exchange ring (9) is taken into account and that - axial forces from the planetary drive (15) of the gas exchange ring (9) as a self-regulating component of the application forces of the gas exchange ring (9) in the manipulated variable calculation System regulation to be included. ( 4th , 17th , 18th ) Internal combustion engine after Claims 21 and 24th , characterized in that - spiral band springs (14) are used as sealing rings, which consist of at least two spring band windings which are conically wound, preformed, circular and face-ground for the resilient property, that - the inner winding of the spiral band springs (14) is completely circumferential the contact sliding surface (9k) slides, which, with its contact pressure on the side part surface, causes the tension of the spiral band springs (14) such that - the outer winding of the spiral band springs (14) on the entire end face carries circumferentially in the puncture base of the side part (13g) that - the Dimensioning and choice of materials for the spiral band springs (14), when subjected to the dynamic combustion chamber pressures on the inner band of the spring, first compress the windings of the spiral band springs (14) in a radially sealing manner due to the surface conditions and the pretension of the spiral band springs (14) is axially stabilized and that - that Contact sliding surface (9k) of the gas exchange ring (9) in egg a mid-level, warm, operational condition is planned. ( 4th , 10th ) Internal combustion engine after Claim 24 , characterized in that the application force of the gas exchange ring (9) relative to the side part ST (13g) by a closed control loop ( 17th ) is determined to which a contact quality as a reference variable and disturbance variables to be taken into account are specified. ( 17th ) Internal combustion engine after Claim 26 , characterized in that - the drive torque (36) of the gas exchange ring (9), which results from the maximum preload of the spiral band springs (14), and - the desired contact friction is established by a safety margin in the preload (19a) full contact of the gas exchange ring (9) with the side part (13g) in the contact sliding surface (9k). ( 17th , 18th ) Internal combustion engine after Claims 1 , 11 and 24th to 27 , characterized in that the algorithm of the control circuit for the application forces of the gas exchange ring (9) also takes the disturbance variables such as fuel rates, speed, supercharger pressures in the inlet duct (12) and number of active combustion chambers into account in relation to one another and is based on the operational results, especially in the Optimized in terms of the delay-free reaction. Internal combustion engine according to the Claims 1 , 11 and 24th to 27 , characterized in that from the analysis of the drive torque of the gas exchange ring (9) and the seismic signals (46) the evaluation of the contact quality including all important operating events, which is decisive for the controlled variable, can be seen. ( 17th ) Internal combustion engine after Claim 1 , characterized in that - the water circuit of the cooling system comprises the 4 main components gas housing (16), side part ST (13g) with the flow around the combustion chambers (8), the housing ring (2) and the side part (13öl) in this order all around by ring lines (24 ), (24a), (24b) and (25) evenly distributed, axially flowed through and that - the cooling of the intake air and the E-EGR components is integrated in the gas housing (16). ( 2nd , 3rd , 4th , 7 , 8th ) Internal combustion engine after Claim 1 , characterized in that both motor housings (16) and (31) are lubricated and cooled by the dry sump method, on the one hand for the gas exchange side (16) with the drive (15) and the bearing (21) of the gas exchange ring (9) and on the other hand for the Eccentric side (31 with the main bearings (29) of the eccentric shaft (7), with bearings (30) for the eccentric ring (1), with the plain bearing of the calottes (5) in the eccentric ring (1) and also the supply via the slide valve (4) the calottes (5) in the housing ring (2). ( 19th , 20 ) Internal combustion engine after Claim 31 , characterized in that - the two partial oil circuits connected in parallel are controlled independently of one another in terms of temperature, that - the bearings are fed by a common pressure pump (42) with variable distribution (43) of the oil quantities when using plain bearings for the eccentric side, - the oil return from the gas exchange side (16) takes place directly into the settling tank (44) due to the gas pressure from this sealed part of the internal combustion engine and that - the suction pump (45) the oil-gas mixture from the eccentric side (31) into the settling tank (44 ) leads back. ( 19th ) Internal combustion engine after Claims 31 and 32 , characterized in that - in addition to the control of the oil temperature (51) and (52) also the oil quantity difference and the gas content (53) and (58) are controlled to improve operational safety and - the necessary control processes such as the control of the oil distributor (43 ) and the suction vacuum on the suction pump (45) by digital data processing in the uniform electronic motor management (54). ( 19th ) Internal combustion engine after Claim 31 and 32 characterized in that - the relative movement of the eccentric ring (1) relative to the separating slide (4) causes an intensive pulsation in the oil-gas mixture of the separating slide (4) - calotte (5) system in that - the suction effect of the separating slide (4) also the check valves (32) and the gate valve-controlled oil drains (61) the oil-gas mixture return from the eccentric side (31) into the settling tank (44) and that - the oil drains (61) by the movement of the gate valve (4) and the calottes (5) release the oil-gas flow from the inner and outer spherical caps (5) during the compression movement of the separating slide (4) and close it during the suction cycle. ( 11 u . 12th ) Internal combustion engine after Claim 31 , 33 and 34 , characterized in that - with the delivery rate of the separating slide relative movement, the series-connected oil-gas flows of both oil circuits of the gas exchange side (16) and the eccentric side (31) are sucked off and fed to the settling tank (44) in that - the oil supply to the gas exchange side ( 16) even when the internal combustion engine is started from the settling tank (44) by the controlled tank pressure (57), that - the control device (54) regulates the vacuum and the gas quantities in the gas housing (16) and eccentric housing (31) by means of the manipulated variables oil quantity , Labyrinth air (23) and air supply through the ventilation valve (55) into the gas housing (16) and / or eccentric housing (31) that - the pumping power of the sliding gate relative movement increases the cooling effect of the dry sump circuits for the gas and eccentric side, - through the controlled suction pump (45) the pumping capacity of the separating slide calotte system is supported that - Both the gas pressures between the sliding surfaces in the separating slide-calotte system (4) - (5) as well as the gas pressures between the eccentric ring (1) and side parts (13) via the slide valve-controlled oil drains (61) and the relief holes (62) of the eccentric ring (1 ) are influenced and that - the loader work is supported via valve (56). ( 20 ) Internal combustion engine after Claim 35 , characterized in that the control device (54) the oil consumption and the blowby amounts from the analysis of the data of both sub-circuits such as pressures (50), (57), (60), flow rates (50), (53), temperatures (44 ), (51), (52) and the oil level and the blowby quantities (56) from the settling tank (44) are used for the automatic improvement of the operating state. Internal combustion engine after Claim 1 , characterized in that - the total fuel injection duration or injection pulse width is divided into at least two pulses and - for these injection periods, the main intake and compression turbulences by 90 ° before and 90 ° after UT and / or the squish turbulence 45 ° before ZOT. ( 21 and 22 ) Internal combustion engine after Claim 1 , characterized in that - the power control is mainly carried out by operating the necessary combustion chambers (8), which work in the optimum map point according to consumption and pollutants, - the required number of combustion chambers (8) is determined by injecting the fuel from the control circuit of the electronic engine management system, optimal fuel quantities are switched on or off that - the required number of combustion chambers (8) are only operated in firing sequences that use all existing combustion chambers (8) in an even firing sequence and that - continuous transitions between the combustion chamber stages of the ZFW by varying boost pressure, EGR -Proportion, injection quantities and timing adjustment (35) are driven, and that - the electric charger is relieved at lower ZFW levels by the cooled, oxygen-rich E-EGR. Internal combustion engine after Claim 1 , characterized in that - the internal combustion engine for uniform operation without chamber shutdown, without throttling, without electric charger, without turbocharger, without control for gas exchange ring application, without timing adjustment (35), without oil pumps (42), (45) and only with oil temperature control is operated and that - with ventilation valve (55), oil suction, vacuum control for gas and eccentric side and oil metering by pressure in the settling tank (44) by the pumping action of the relative movement of the isolating slide (4). ( 21 ) Internal combustion engine according to one or more of the preceding claims, characterized in that - for comfort applications with high efficiency, the extended premixed combustion by: injection in the intake and compression stroke, P1 and P2, combustion in the effective combustion chamber separated from the work space (3) ( 8), Combustion in combustion chambers (8) <20 cm ³ , with an electric charger, geometric compression greater than or equal to 12: 1, air ratio λ greater than or equal to 1.0, that - with power control through flexible switching off and on of the ZFW as well as synchronous gas change time adjustment (35) and that - serial oil extraction is used in the dry sump process. ( 20 ), ( 21 ) Internal combustion engine according to one or more of the preceding claims, characterized in that the combustion type HCCI is used for the entire performance spectrum with geometric compression by 16: 1, λ> 1.2, EGR> 20%, that - driven by injection during the intake cycle is that - the electric charger is used, - that when the internal combustion engine is started in the closed control loop of the central engine management with electrical ignition sparks, that - with the choice of working chamber ignition sequence ZFW with continuous, minimum number of chambers per revolution, throttle-free and with increasing charger pressure is driven until the seismic signal (46) from the actuator (19) or another seismic signal provides usable and resilient auto-ignition events including ignition delay for the further control of engine operation and that - with these secured settings the continuously optimizing driving style with the new ones stored values for the number of active working chambers (3) required depending on the load is continued and that - the auto-ignition data is included in the control program of the engine management (54) for automatic program optimization. Internal combustion engine after Claim 41 , characterized in that - when auto-ignition is reached, part of the total fuel injection rate of less than 10%, branched off from the injection volume P1 or P2, for the injection 10 ° EW v. ZOT serves and that - the temporal and quantitative values of the injection sequence after reaching the seismic auto-ignition signal (46) or another signal are used automatically to shift the heating maximum into the range 10 ° ... 20 ° EW according to ZOT. (see 21 and 22 ) Internal combustion engine according to one or more of the preceding claims, characterized in that - the known diesel combustion method with a glow plug is used instead of the spark plug (11) and - the analysis of the seismic signal (46) or another signal for regulating the optimum diesel injection time at the heating maximum in the range 10 ° to 25 ° EW according to ZOT. Internal combustion engine after Claim 43 , characterized in that power control is used by flexible working chamber switching off and on ZFW. Internal combustion engine according to the Claims 43 and 44 , characterized in that - a subset of the metered fuel already in the intake stroke and / or in the range 160 ° EW v. ZOT is injected that - this partial quantity is increased depending on the operating temperature up to the soot and / or knock limit and - with the rest of this partial quantity the injection time of the main fuel quantity before ZOT for the heating maximum in the range 10 ° to 25 ° EW according to ZOT is regulated. Internal combustion engine according to one or more of the Claims 39 to 45 , characterized in that, in addition to the common fuels, gaseous fuels, CNG or CO2-neutral new developments, for example from the field of OME (oxymethylene ether), are used. Internal combustion engine according to one or more of the preceding claims, characterized in that - a 2-cycle process by programming the gas exchange ring (9) by overlapping gas exchange times in the region of UT with AÖ 45 ° EW before UT, EÖ 15 ° before UT, AS 30 ° EW to UT, ES 60 ° EW to UT enables the compression effect to be significantly improved by high-pressure charging using an electric charger, that the power control is supported by ZFW working chamber selection, that the type of combustion HCCI and / or spark plug spark ignition is used for the entire power spectrum that - with geometric compression around 16: 1, with λ> 1.2, EGR> 20% and - with the use of the auto-ignition timing by analyzing the seismic signal (46) from the actuator (19 ) or another signal, the optimal ignition timing including ignition delay is determined and included in the control program of the engine management (54) for program optimization. ( 23 )

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