JPH01163402A - Rotary machine - Google Patents

Abstract

PURPOSE: To avoid excessive abrasion between a rotor and a cavity wall by disposing a planetary gear device or an epicyclic gear device between the rotor and a main crank shaft. CONSTITUTION: An internal ring gear 37 meshing with a pinion gear 38 at a gear ratio of 3:2 is affixed or fixedly attached to one side of a rotor 21. An integral cluster gear device is constituted by the internal ring gear 37 and a gear 47 having a hollow shaft rotatable about a main crank shaft 24. The gear 47 meshes with a gear 51 which constitutes another cluster gear device together with a gear 52 having another shaft 42. The gear ratio of the gear 47 to the gear 51 is fixed to 21. The gear 52 is affixed or fixedly attached to the main crank shaft 24 and meshes with a final pinion gear 48. The gear ratio of the gear 51 to the final pinion gear 48 is fixed to 2:1. Therefore, a clearance between the rotor 21 and a wall of a housing cavity 20 can be maintained constantly and permanently during relative rotations.

Description

DETAILED DESCRIPTION OF THE INVENTION [Field of Industrial Application] The present invention relates to a rotary mechanism. More particularly, rotary internal combustion engines, rotary equipment/machines such as rotary compressors, rotary pumps, rotary cutting tools or lathes, and any fuel suitable for rotary internal combustion engines, for land, sea or air transport or other Relating to a rotary machine in the sense of including a rotary device of an aircraft engine or any future flying vehicle for any special purpose. In this specification, for simplicity,
These are called rotary machines.

[Conventional technology]

A rotary machine of the aforementioned type has an external element with axially spaced end walls and a curved or axis-parallel periphery, and an axially spaced end face and a curved or axis-parallel periphery. It consists of an internal element with a periphery parallel to .

These elements are referred to herein for simplicity as the housing and rotor, respectively.

The housing is a two-apex type rotor (2apex type rotor).
Epicyclic for Rotor
llc) shaped cavity or 3 apex rotor (
3 apex rotor).

In such rotary engines mounted eccentrically on the main crankshaft, an internal ring gear is usually fixed or fixed within one side of the rotor and meshes with a pinion gear having a hollow shaft that rotates freely within the main crankshaft. In particular, in rotary machines with a three-apex type rotor, the gear ratio between the internal ring gear and the pinion gear is fixed at 3:2, so that the pinion needs to be fixed or fixed to the housing frame. The aforementioned gear ratios therefore constrain the diameter of the main crankshaft due to a certain degree of eccentricity in its design. This arrangement of fixing the pinion to the housing frame, depending on the strength of the cavity walls, can result in force transmission to the rotor's strong pressures, which can occur immediately after ignition/combustion, especially in the extreme conditions under which the engine is operated. , it is subjected to the impact of a strong force generated by the expanding gas. Sooner or later, such conditions result in extremely severe wear along the line of contact between the cavity wall and the rotor, thus shortening the life and durability of such engines. Such a rotor with axially spaced end faces and an axis-parallel peripheral wall (hereinafter also referred to as a rotor with a flat outer surface or a flat rotor for simplicity) is defined by its geometrical Due to the condition, so-called corner seal leakage is considered one of the most serious problems to be solved.
e). Due to such limited dimensions of the main crankshaft, fixation of the pinion gear to the housing frame, and corner seals, such typical rotary engines suffer from relatively low efficiency, high fuel consumption, and, as is widely known, It was characterized by high emissions and excessive wear.

[Problem to be solved by the invention]

The present invention overcomes the aforementioned poor performance by using a large pinion gear and allows the pinion gear to rotate and transmit power directly to the main crankshaft along the line of contact between the rotor and the cavity wall. The use of a radially curved apex rotor section as well as a radially arcuate housing cavity wall eliminates corner sealing problems found in conventional models. The object is to provide a novel device in which a sealing element is inserted between them.

[Means to solve the problem]

These purposes are addressed, for example, by European Patent Application Section 87.
No. 201780.1 and U.S. Patent Application Section 09.8.1
This is achieved by installing a planetary gear system or an epicyclic gear system instead of installing meshing gears as described in each specification of No. 89. Their gearing fixes the speed ratio to 3 or 1:2, as required to maintain the clearance between the rotor and the housing cavity wall permanently and stable or constant during relative rotation. Therefore, it is installed between the rotor and the main crankshaft. A permanent, stable or constant clearance as described above avoids any direct contact of the rotor with the housing cavity, especially in the extreme conditions under which the engine is operated.

In a preferred embodiment, the arm of the planetary gearing or epicyclic gearing is constructed integrally with the pinion gear, whereby the planetary gearing adjusts the speed ratio of the rotor and the main crankshaft to the epicyclic housing cavity. and 1:2 for a 2-apex rotor combined with a 20-tube epitrochoidal housing cavity, and 1:3 for a 3-apex rotor combined with a 20-tube epitrochoidal housing cavity.

Unlike conventional devices in which the pinion gear is fixed and fixed to the housing frame, whereby the pinion always remains in its rest position, in the present invention the pinion rotates or is rotated according to the interrelationship speed between the gears, thus The possibility of the rotor pressing against the cavity walls due to strong dynamic forces to transmit forces to the main crankshaft of the engine under extreme conditions, thereby causing wear, may be avoided.

The rotation of the pinion is fixed at a ratio of 1/4 for a 2-apex rotor and 1/9 for a 3-apex rotor. That is, this is the main crankshaft of a machine with a 2-apex type rotor.
The pinion rotates up to 90" for every 0° rotation, and the pinion rotates up to 40" for every 360@ rotation of the main crankshaft of a machine with a 3-apex rotor.
'', whereby the rotor obtains its proper speed. Based on such a configuration, it is possible to use a large internal ring gear that is fixed or fixed to one side of the rotor.

the ring gear is configured with a gear ratio of 3:2 to the intermeshing pinion gear for a 2-apex rotor, and a 4:3 gear ratio to the intermeshing pinion gear for a 3-apex rotor; Such a gear ratio makes it possible to employ larger dimensions of the main crankshaft diameter, which results in better and stronger performance. Further, based on such a configuration, if necessary, for example in an internal combustion engine, the shape is curved in the radial direction and extends continuously from one apex to another adjacent apex, and the intermediate part between the two adjacent apexes, : This makes it possible to adopt an apex-type rotor part whose curved shape is minimized. The radially curved axle-shaped rotor shape described above is not necessarily required when the configuration is employed in compressors, pumps, cutting tools, and the like.

In the case of internal combustion engines, the outer surface of a radially curved three-apex rotor has channels formed between each of two adjacent curved apexes to obtain the appropriate compression ratio required by the manufacturer. while each apex of the radially curved rotor is provided with sufficient grooves, such as beveled or regular grooves, for suitable rings and sealing element mounting seats.

Optionally, for machines with two apex rotors, the flow paths described above for machine configurations with three apex rotors are not required. This is because, for the same purpose, the curvature of the outer surface of the two-apex rotor can be tailored to the requirements for a suitable compression ratio.

Particularly for machines with two-apex rotors, inlet and outlet valves may be provided which are driven by one or more camshafts with a speed ratio of 1:4 to the rotation of the main crankshaft.

Thus, with the present invention, an effective gap is created between the cooperating features of the radially curved apex rotor and the radially arcuate housing cavity wall, which remains constant during any relative rotation of the rotors. This ensures that the sealing element functions properly and prevents any leakage of pressure from one working chamber to another by its own spring force, thus reducing the durability of the machine. Maintain an acceptable normal wear rate for the vine. In this regard, in the present invention, the inner surface as well as the seal ring is coated in order to obtain a smooth and hard chromium-plated surface that has good affinity with lubricating oil and greatly reduces the wear rate of the seal ring. A chromium plated radially arcuate housing cavity wall may be employed.

In particular, for a 3-apex rotor, in the present invention, instead of configuring a curved or flat rotor to be a 3-apex type with a 30-b shaped external surface, it is configured to have a 3-apex type but a 60-b shaped external surface. may be configured. Such a configuration allows the three-apex rotor to completely sweep compressed fluid or gas into the outlet channel of the housing cavity, such that the same outer surface is connected to the inlet stream adjacent to said outlet channel. Fresh fluid or gas is received from the channel and advanced to the suction and compression chambers, respectively.

When such a configuration is applied to an internal combustion engine, in the present invention, a flow path similar to that described above is provided between two adjacent channels in order to adjust the compression ratio as required by the manufacturer.
may be formed between each of the two apexes, whereby the flow path advances the remaining combustion gases;
further mixing with the newly inserted air and fuel mixture through the adjacent inlet channel.

For rotary machines with either two-apex rotors or three-apex rotors, a planetary or epicyclic gearing system may be installed between the rotor and the main crankshaft.

The planetary gear system or epicyclic gear system usually consists of three different gears, such as a sun gear, a planet gear, and a stationary external ring gear. The sun gear is the central gear of the device, while the planet gear is a mating gear between a stationary ring gear and said sun gear, which rotates in the opposite direction to the main crankshaft, so that the arm of the planet gear is the same as the main crankshaft. Allows you to rotate in any direction. In this particular construction, in the present invention, the planet gear may be integrally constructed with a pinion gear meshing with an internal ring gear fixed to one side of the rotor, while the sun gear is connected to the main crankshaft by an involute spline gear or the like. It may be fixed or fixed to. With this configuration, the rotation of the main crankshaft is integrated with the rotation of the rotor, and the gear ratio reaches the aforementioned speed ratios such as 1:2 for the 2-apex rotor and 1:3 for the 3-apex rotor. Fixed at the appropriate required gear ratio needed to

For a two-apex rotor with an internal ring gear and its pinion based on a gear ratio of 3:2, a suitable planetary or epicyclic gearing system has a sun gear, a planet gear and a stationary external ring gear with a 1:2 gear ratio.
It is configured to be fixed according to the gear ratio of 1:3. With such a configuration, the planet gear arm rotates 9 for every 360' rotation of the main crankshaft.
06 rotates or is caused to rotate.

For a three-apex type rotor with an internal ring gear and its pinion based on a gear ratio of 4:3, a suitable planetary or epicyclic gearing system has a sun gear, a planet gear and a stationary external ring gear with a ratio of 1:3.
It is configured to be fixed according to a gear ratio of 1:8. With such a configuration, the arm of the planet gear rotates 40° for every 360° rotation of the main crankshaft.
``To rotate or be caused to rotate.

If a gear ratio of 1=8 between the sun gear and the stationary external link gear is impractical in terms of construction, the invention provides:
Instead of configuring the planet gears based on a 1:1 gear ratio to the sun gear or a 1:8 gear ratio to the stationary external, the small gear meshes with the ring gear based on a 1:4 gear ratio, and the large gear meshes with the sun gear based on a 1:4 gear ratio. A cluster gear device is constructed of two integral gears, a small gear and a large gear, which mesh at a gear ratio of :2. Such an arrangement allows the planet gear arm to rotate or be rotated by 40° for each 360° rotation of the main crankshaft.

In theory of motion, only one meshing gear is required as a planet gear, but by using three types of gears, a better balance is achieved and the load is evenly distributed between the gears, thus reducing the Allows the use of smaller and thinner gears.

Therefore, the above-mentioned planetary gearing or epicyclic gearing has many advantages over meshing gears, especially stable rotation, central axis precision, and simple construction.

Particularly in configurations with a radially curved apex-type rotor and a radially arcuate housing cavity, the configuration of the housing cavity may include two or more sections transverse or parallel to the axial shaft, as the case may be. shall be provided with suitable gaskets, rubber or other suitable seals to prevent any leakage of pressure or cooling water as well as leakage of lubricating oil from one working chamber to another. It may also have a different structure.

Regarding the configuration of the housing cavity, a speed ratio of 1:3 to the main crankshaft for a 3-apex rotor or a 2-apex rotor, for either a rotor with a radially curved apex or a flat surface. Based on a speed ratio of 1:2 with respect to the main crankshaft (similar to the outer envelope of the rotor, in order to draw the correct and precise shape, including the permissible or permissible clearance determined by the manufacturer), the engine A special cutting tool constructed on the same principle as , but with a fixed or fixed precisely sized cutting blade may be used for the cutting and precise formation of the internal housing cavity. The cutting tool should be configured based on the same degree of eccentricity as the engine.

Special similar cutting tools for 3-apex type rotors with a 60-b type external surface, whether of radially curved or flat type, are possible based on the same principle, but with suitable Unlike cutting tools for housing cavities that cut while rotating at speed, this typical rotor cutting tool is of a static configuration.

In preferred embodiments, internal ring gears, pinions, as well as planetary or epicyclic gearing are used.
With a similar gear principle, such as a gear as an intermeshing gear device, the European Patent Application No. 87.201780
．． No. 1 and US Patent Application No. 098.189, machines may be constructed based on different gear ratios determined or resulting from calculations based on the following equations:

1.1. G, P, -l-P 1, [, G, b However, 1.1. G, P, : Pitch diameter of internal involute gear pinion, 1, T, G, : Pitch diameter of internal involute gear, a/b: Additional revolution of internal involute gear per revolution of the main crankshaft, P : The basic ratio for each particular type of rotary machine is 1/2 for a rotary machine with a 2-apex rotor and an epicyclic howling cavity, and 1/2 for a rotary machine with a 3-apex rotor and a 20-tube epitrochoidal cavity. 2/3 for rotary machines using housing cavities.

Regarding the above formula, the gear ratio of the dog gear device may be determined based on the following calculation.

a/b -1,1,G,P,/1.1. G, Xc/d
Xe/f where c/d and e/f are the gear ratios of the meshing gears. Also, if more gears are required to obtain the correct gear ratio, the above calculation can be extended as follows.

a/b -1,1,G,P,/1.1. G, xc/d
Xe/f

〔Example〕

Next, embodiments of the present invention will be described based on the drawings.

1 is a longitudinal sectional view of a rotary machine with a radially curved two-apex rotor, a radially arcuate housing cavity and a meshing gear provided therebetween; FIG. A cross-sectional view taken from the line (I)-(11) in the figure and partly from the line (I)-(I[) in FIG. 1, FIG. 3 shows a two-apex rotor combined with an epicyclic housing An explanatory diagram showing detailed movements,
FIG. 4 is an illustration showing two two-apex rotors combined in one machine, and FIGS. 5-6 are rotary machines each having a curved two-apelles rotor and a curved epicyclic housing cavity. FIG. 7 is an explanatory diagram showing a planetary gear device applied to a flat two-apex type rotor and an epicyclic housing cavity, and is configured for a vehicle air conditioner. A longitudinal sectional view of the rotary compressor of the invention, FIG. 8 is a longitudinal sectional view of a special cutting tool for forming the housing cavity, and FIGS. 9 and 10 are a curved 3-apex type rotor and a curved 20-b type epitrochoidal housing cavity, respectively. 11 and 12 are explanatory diagrams showing a planetary gear device applied to a rotary machine having a rotary machine having a rotor having a 3-apex type and a 60-beam external surface, and a 20-beam type epitrochoidal housing cavity. In the cross-sectional view shown in Fig. 11, 1 for the main crankshaft is shown.
13-14 are perspective views showing a radially curved three-apex rotor equipped with a meshing gearing according to the invention; FIG. The exact position of the curved apex of the rotor during any relative rotation based on a speed ratio of 1:3 with respect to the main crankshaft is shown, and FIG. A partially sectional perspective view showing the entire machine with a mold rotor and its housing cavity and a meshing gear system, Figures 1a to 1d each relate according to the theory of motion related to the present invention. It is an explanatory view showing relative movement of parts.

1-2, the rotary internal combustion engine of the present invention is provided with two rotors having two radially curved apexes and having a curved housing cavity head. The rotor is connected to the main crankshaft (24J
attached to each eccentric hubshaft made and constructed integrally with the rotor and rotated freely by metal bearings between the rotor and the eccentric hubshaft and between the main crankshaft and the housing frame. The structure is as follows.

The rotor is provided with side seal elements connected to an apex seal element and to a lubricating oil scraper ring.

The curved housing cavity is provided with inlet and outlet flow passages (30) controlled by a valve (31) supported by a coil spring (32).
) is driven by a camshaft (3B), a rocker arm (33) and a connecting rod (34).

The engine is also provided with an ignition mechanism using a spark plug (35) fixed or fixed to the housing frame (1), the housing frame head has a supporting body, and the supporting body serves as a lubricating oil tank (39). also works.

As a cooling device, the housing frame is also provided with a cooling water flow path (40), similar to the conventional configuration.

An internal ring gear (37) is fixed or fixed to one side of the rotor (21) and meshes with a pinion gear (38) in a gear ratio of 3:2. The internal ring gear (37) constitutes an integral raster gear device together with a gear (47) having a hollow shaft that freely rotates around the main crankshaft Q4 by means of roller bearings (41).

Said gear (47) meshes with a gear (51) which together with a gear (52) having a separate shaft (42) constitutes another cluster gear arrangement.

The gear ratio between gear (47) and gear (51) is fixed at 2:1.

The gear (52) meshes with a final pinion gear (48) that is fixed or fixed to the main crankshaft (24) with an involute spline and reinforced with a special lock nut (49), and the gear (51) and the final pinion gear (48) are The ratio is fixed at 2:1.

The shaft (42) of the cluster gear device is provided with a bearing (43), and the end of the shaft is attached to the housing claim (2) and the gear cover (50). At both ends of the main crankshaft (24) are mounted ball bearings (44), lubricant seals (4B) and seal covers (45) to prevent any leakage of lubricant from the engine.

In FIG. 3, the detailed movement of the rotor (21) within the housing cavity (2) is shown precisely on the basis of a speed ratio of 1:2 between the rotor and the main crankshaft (M).

The housing cavity (2) has an epicyclic shape and a permanent or constant gap between the rotor (2υ) and the housing cavity (2) is made possible by such a configuration.

Figure 4 shows the first and second hub shafts in the same state as shown in Figures 1 and 2, with the eccentric hub shafts making an angle of 180° to each other.
FIG. 3 is a diagram showing the exact position of each rotor shown in the figure;

In such a configuration, the forward rotor with an apex seal element is mounted on the eccentric hubshaft via a bearing, and the main crankshaft C4
is driven at a speed ratio of 1:2. The rear eccentric hubshaft is 11 times larger than the front eccentric hubshaft.
Positioned at an angle of 10', the rear portion of the housing cavity is formed higher than the front portion due to a predetermined degree of eccentricity for balanced rotation and ignition. Due to such conditions, the inlet and outlet channels of the front part (30/II) are relatively higher than the inlet and outlet channels of the rear part (307n), while the rear housing cavity (20/n '') is Front housing cavity (20/I)
be higher than

Figures 5 and 6 are explanatory diagrams showing a planetary or epicyclic gear system used in a similar radially curved two-apex type rotor combined with a radially arcuate housing cavity. .

In such a configuration, the main crankshaft (324)
A sun gear (348) fixed or fixed to is meshed with three planet gears (382) attached to the arm shaft (361) so as to rotate freely, based on a gear ratio of 1:1. The three planet gears (
3B2) is an external ring gear (3B2) based on a gear ratio of 1:3.
59) are interlocked with each other. By stacking the planet gears, the speed ratio of the arm (360) is reduced by 1.
: (3/1+1) -1:4 or equal to 90° for every 360° rotation of the main crankshaft.

Also, pinion gear (38) and internal ring gear (37)
Due to the gear ratio of 2:3 between
/3) Rotate or be rotated to X380'-120'. The arm is integrated with a pinion with a gear ratio of 2:3, so that the internal ring gear rotates or rotates 2/3X90°-60' as an additional rotation for every 360' rotation of the main crankshaft. It will be done. By adding an additional rotation of 60" to its own 120° rotation, the rotor (21) has a total of 120' +8 for every 360° rotation of the main crankshaft.
0°-180° rotation, speed ratio 1 required with 2 apex rotor and epicyclic housing cavity
:It will follow exactly 2.

FIG. 7 shows a rotary compressor based on the principles of the present invention constructed for a vehicle air conditioning system, and in order to show how compact and effective the device of the present invention is for such purpose, 1: Designed to actual dimensions of 1.

Such a compressor comprises a two-apex rotor (421) with a flat outer surface provided with suitable sealing elements (427).
), and an integral internal ring gear (437) is constructed of the same material and meshes with the pinion gear (438) based on a gear ratio of 2:3. The rotor (421) is mounted on an eccentric hub shaft made integrally with the main crankshaft (424) so as to rotate freely via a roller bearing (422) installed therebetween. .

The pinion gear (438) is manufactured integrally with the arm of the planet gear (462), and the pinion gear (438)
The arm shaft (4
61).

The sun gear is fixed or fixed to the main crankshaft by an involute spline and meshes with the three planet gears based on a gear ratio of 1:1. The three planet gears also mesh with an external ring gear (459) that is fixed or fixed to the housing frame.

With such a configuration, the arm is attached to the main crankshaft (42
4) is rotated or caused to rotate by 90 degrees per one rotation. That is, to obtain a speed ratio of 1:2, the rotor rotates 60 degrees as may be required as an additional revolution for one revolution of the main crankshaft.

The main crankshaft (424) is provided with a lubricating oil hole through the central part (453), thereby ensuring sufficient lubrication of the roller bearing (441) installed in the hollow shaft of the pinion gear (438), and , coil spring (457), carbon seal (4467C), stationary seal sheet, rubber gasket (45g), and retaining ring (4
59) to lubricate the rotary seal device consisting of. Both sides of the main crankshaft (424) have snap rings (45
9) in the front ball bearing (444/
P) and the rear ball bearing (444/R), and is closed with an end cover (445) after being sufficiently lubricated with special lubricating oil. In the forward part, a balance counterweight (464) is fixed or fixed to the main crankshaft by a lock nut (449).

The outer part of the housing includes a magnetic field coil (461),
A freely rotating pulley seat arrangement arranged on a cylindrical roller bearing (45B) for acting in cooperation with the clutch arrangement (455) is fixed. The cylindrical roller bearing is fitted with a special lock nut (480).
is fixed and fixed to the housing frame by a front hexagonal nut (465), while the clutch device is fixed and fixed to the main crankshaft (424) by a front hexagonal nut (465).

In the rear part, the compressor has a Schrader (schr)
ader) (454) is also installed, and a cylindrical plate valve (483) is installed in the inner part.

FIG. 8 is an illustration showing a special cutting tool made to precisely cut or shape a radially arcuate housing cavity or flat interior surface for a two-apex rotor or a three-apex rotor.

Said device of the invention consists of a similarly shaped rotor (221) with a cutting blade (254) fixed or secured by bolts and nuts (255).

The rotor is attached to an eccentric hub shaft (223) made integrally with the main crankshaft (224), and is attached to the aforementioned (237'), (238), (24).
7) and (251) and (252) and (24
8) by means of meshing gears, in accordance with the respective gear ratios as required for each type of machine, a speed ratio of 1:2 for a two-apex rotor and a speed ratio of 1:3 for a three-apex rotor. Rotate with.

In such a configuration, the main crankshaft (224)
is held by two ball bearings (244), connected to a pinion lock nut (249) in the front part, and closed with some kind of hexagonal nut in the rear part. To drive the cutting tool, a pulley is installed between both bearings and is fixed to the main crankshaft (224) by an insertion key (25B).

The ball bearings are located on both sides of the main frame (257), which is connected to the cluster gear system (24).
2) configured to accommodate one side of another hub shaft; The other side of the separate hub shaft is supported on a special separate stand (258) which is fixed or secured to the main frame by bolts and nuts.

Figures 9 to IO show curved 3-apex type rotors and 2
FIG. 2 is an explanatory diagram showing a planetary gear device applied to a rotary machine having a curved epitrochoidal cavity (1) of a 0-b type. The planet gear according to the present invention is a small gear.
(382/I) and a large gear (362/n), the sun gear (348)
Based on the gear ratio fixed at 1:2 between the gear (3B2/■) and the gear (362/I) and the ring gear (359), It meshes with the sun gear (348) as well as the external ring gear (359). The sun gear is fixed to the main crankshaft by an involute spline and reinforced by a special lock nut (349). By stacking the planet gears, the speed of the arm is reduced to 1:(2×4/l)+1-1:9, or equal to 40'' for 360' rotation of the main crankshaft.

By setting the gear ratio between the pinion gear (38) and the internal ring gear (37) as 3:4, the rotor (2
1) is (1-3/
4) Rotate or be rotated to X 380"-90@. By rotating the arm by 40 degrees as described above,
The rotor has 3/4 rotation for one rotation of the main crankshaft.
X Additional rotation up to 40°-30' is achieved by pinion gear (3
8) is given by Therefore, by adding said 30° additional rotation to its own 90@ rotation, the rotor will rotate for a total of 90°+ for one revolution of the main crankshaft.
30 DEG = 120 DEG rotation, which is exactly in accordance with the 1:3 speed ratio required in a typical rotary engine such as that described above with a 3-apex rotor and a 20-tube epitrochoidal housing cavity.

11-12 are illustrations of a typical rotary machine having a 3-apex rotor with a 60-lobed exterior surface and a 20-lobed epitrochoidal housing cavity, with the rotor relative to the main crankshaft. The gear ratio is fixed at 1:3, and its movement can be seen from Figure 11. Such a configuration allows for a large space to be roamed in the apex part which cooperates with the cavity wall to prevent leakage.

13-14 are perspective views showing the rotor with meshing gears according to the invention and the exact position of the apex rotor at a speed ratio of 1:3. When compared to a conventional configuration with a stationary pinion gear fixed to the housing frame for the same size rotor, the configuration of the present invention has a shorter horizontal direction of line (c4)-(b2) as shown in FIG. It has not only a length but also a shorter degree of eccentricity.

FIG. 15 is a partial cross-sectional perspective view showing the overall concept of the present invention, showing the rotor (121), the radial apex seal (12g), the curved housing (120), the side seal element (127), the internal ring gear ( 137
), pinion gear (13B), meshing gear (14
7) , (14g) , (151) and (152)
, main crankshaft (124) and eccentric hub shaft (123), flywheel (1B4), inlet channel (tea), outlet channel (185), lubricating oil tank (195), oil filter (190), cooling A fan (180), a generator (170), etc. are shown.

16a to 16d are diagrams for explaining the theory of motion.

Next, the motion theory related to the device of the present invention will be explained.

Figures 1a to 1d are diagrams showing the motion theory of a preferred embodiment of the present invention, and in the illustrated rotary engine, 1.1. G, (internal involute gear) (400
) is fixed to the rotor (200) and has a hollow shaft. G, P, (internal involute gear pinion) (500) mesh with each other. E, H.

S, M including (eccentric hub shaft) (150),
C.S.

(Main crankshaft) (100) is 1.1. G.P.
rotate freely through the

In FIG. 16a, 1.1. G, P, (500) is 2:
Based on the gear ratio of 3, 1,1. G, (400) is meshed with 1.1. G, P, (500) has a hollow shaft through which M, C, S, (100) can rotate freely. In this case, 1.1. G, P, (50
0) is fixed or fixed to the housing frame as in the conventional configuration.

Based on the gear ratio of 2:3, M, C, S, (too)
/E, I(, S, (150) for one rotation (360°), rotor (200)/1.1.G, (400)
rotates (1-2/3) x 380°=120”,
or rotated. This means that M, C, S, (1
00)/E, H, S, (150). Rotor (
200)/1.1. G, the speed ratio of (400) is 120
':380@-1:3. It means that.

The contact points of both pitch circles are 1.1. G, (400
) and point (c) belonging to the pitch circle of 1.1. G, P
, consists of points (P) belonging to the pitch circle of (500).

In Fig. 1ea, M, C, S, (IOQ)/P, .
H,S.

(150) is rotated 90° (α-90°), so E, H, S, the center point (03) of (150) is (0
Move to 31). +: 1. G, P, (500
) is stationary, so the point (P) remains at its original position, but the point (c) moves to a new position (cβ) (
kuβ−113×kuα■30°).

In Fig. ieb, 1.1. G, P, (500) is 1.1. based on a 3:4 gear ratio. G, (400) is meshed with 1.1. G, P, (500) are still fixed or fixed to the housing frame.

With such a gear ratio of 3:4, M, C, S, (100
)/E, H, S.

One rotation of (150) causes rotor (200) /1.1. G
, (400) is (1-3/4) x 360°-90
"Rotate or be caused to rotate. Therefore, the first
In figure 6b, M, C, S, (100)/E, H,!
3. (150) The point (c) rotates by 90” and the point (
cφ), and point (P) is still at the original position (φ−1/4x<α−22°5″).

However, when using a 3-apex type rotor and a 20-b type epitrocoil housing cavity, the speed ratio of the rotor (100) must be maintained at 1:3, so the new point (c) The position must be at point (cβ) (β−30°).

The distance between the point (cφ) and the point (cβ) in FIG. 16b is the distance between the rotor (200)/1.1. G
, (400) is the rotor (200) and M, C, S,
(100), the rotor (200)/1.1
．． G.

(400), and by means of said meshing gears the rotor (200) can always reach the exact position of point (cβ) within a predetermined time for each rotation mentioned above. The additional distance from this point (cφ) to the point (cβ) can be expressed as a ratio by the laser (Ras).
er) is expressed as alb in the formula. In Figure teb, the distance from point (cφ) to point (cβ) is expressed in degrees as 30' - for every 90'' rotation of the shaft.
22,5'-7,5'. Therefore, set this to 3
Calculated on the basis of a complete rotation of 60°, the distance is (
360@: 90”)
In the case shown in the figure, the quotient of alb is 1112
is equal to

The above formula is based on European patent application section 87゜201
No. 780.1 and US Pat. This formula was created in order to minimize the number of gears.There are many ways to determine the gear ratio for the same purpose. As mentioned above, gear calculation ↓ If this laser formula is not used, there is a possibility that the quotient of alb will not match the exact number depending on any combination of gears installed. Therefore, the outer envelope of rotation of the rotor does not have exactly the same shape as the 20-tube epitrochoidal / 11) During all relative rotations, a permanent gap of 1 cannot be maintained.In the previous statement, the permanent gap i during all relative rotations of the rotor (200) is always M, C, S,
This is possible only if a speed ratio of 1:3 to (too) is maintained.

Furthermore, the present invention is applicable to other rotary types such as 2-apex rotors and 4-apex rotors.

For simplicity, the basic ratio for a particular type of rotary (e.g. 1 for a 2 apex rotor / 2.3 for a 2 apex rotor / 3 for an apex rotor 213.4 for an apex rotor)
14) are each expressed as (P) here, as can be seen from the above equation.

Rotor (200)/1.1. G, (400) and M, C,
S, (100) due to the meshing gear installed between the
Based on the speed ratio of 3:4, so that point (cφ) can reach the position of point (cβ), 1.1. G.P.

(500) are rotated in the same direction.

1.1. The movements of G, P, (500) are from 1ee to IB
d is shown in Figure d.

In FIG. 1ee, +y+, c, p, (56o), together with one of the meshing gears, are mounted in a single hollow shaft through which they rotate or are caused to rotate according to the appropriate speed ratio. 1 with 3:4 gear ratio
, 1. G, (400) and 1.1. G, P, (5
00) for such rotary machines with a/b
Since the quotient of is 1112, 1.1. G, P, (500
) is M, C, S, (100)/E, H, S, (15
l/12X4/l x 360' for one rotation of 0)
- rotated or caused to be rotated to an angle of '40'';
This is a ratio of 1/9. The number 1/9 in such a ratio can be easily decomposed into 1/3X1/3, which means 1.1. G, P, (500) and M, C, S, (10
Separate meshing gears with 0) are 1:3 and 1, respectively;
Means fixed at a gear ratio of 3 (minimum gear for space efficiency).

In Figure 16c, M, C, S, (100) are 90
' Since L does not rotate, the new position of point (P) is point (
Pi), and its position is 90'/380' in the same direction.
X40"-to', and the actual point after one revolution (
The position of P) becomes point (P2), which is 40° away from the original position.

In a rotary machine with a two-apex rotor and one evicyclic housing cavity, the figure is 1/4, which can easily be broken down into fixed gear ratios of 1:2 and 1:2, respectively, and 3. Apex type rotor and 40
In the case of a block-shaped epitrochoidal housing, the number is 111B, which can easily be broken down into fixed gear ratios of 1:4 and 1:4, respectively.

1.1. , G, P, (500) and meshing with it 1.1
．． Based on the gear ratio of 3:4 between G, (40(1)), the diameter of M, C, S, (100) can be constructed larger than in the conventional device. Such a large M, C, S, (100) is shown in Fig. 1ed, which naturally allows the machine to withstand larger loads.□

[Brief explanation of the drawing]

FIG. 1 is a longitudinal sectional view of a rotary machine having a radially curved two-apex rotor, a radially arcuate housing cavity, and a meshing gear provided therebetween; FIG. A cross-sectional view taken along the line fI)-m in FIG. 1 and partly along the line (Il)-(I[) in FIG. 1; FIG. An explanatory diagram showing detailed movements. Figure 4 is an explanatory diagram showing two 2-apex rotors combined in one machine. Figures 5 and 6 are a curved 2-apex rotor and a curved evicyclic rotor, respectively. FIG. 7 is an explanatory diagram showing a planetary gear device applied to a rotary machine having a flat two-apex type rotor and an evicyclic housing cavity, and is used for a vehicle. FIG. 8 is a vertical cross-sectional view of a rotary compressor of the present invention configured for use in an air conditioner; FIG. 9 is a vertical cross-sectional view of a special cutting tool for forming a housing cavity; FIG.
Figures 1 to 10 are explanatory diagrams showing a planetary gear system applied to a rotary machine having a curved 3-apex rotor and a curved 20-tube epitrochoidal housing cavity, respectively, and Figures 11 to 12 are respectively 3-apex type rotors. A cross-sectional view of a rotary machine having a rotor with a 60-bump external surface and a 20-bump epitrochoidal housing cavity, FIGS. FIG. 15 is a perspective view of the rotor, partially in section, showing the entire machine according to the invention with two radially curved 3-apex rotors and their housing cavities and with a meshing gear arrangement. Cropped perspective view, 1st ea~
Each LED diagram is an explanatory diagram showing the relative motion of related parts according to the motion theory related to the present invention. (Main symbols of the drawing) ■: Housing ring cavity α: Rotor (221: Main crankshaft patent applicant Sofiyan Ajwinata No. 5 (branch) Purification of the drawing (no change in content) Fang 6 Purification of the drawing Plan to change to O 8 times 9M Engraving of drawings (L with changes to content) Fig. 10 Engraving of surface 120 - Engraving of m side (Contents l2 unchanged 1312 14th same O 16a Support 16b ( Support) O 16c Skin 216d Oral procedure amendment written form) January 18, 1999

Claims (1)

[Claims] 1. A radially curved or arcuate housing cavity with an epicyclic shape or an epitrochoidal inner wall shape with two and three lobes and (n+1) radially curved lobes. a rotor installed in the cavity and capable of planetary movement (where n is an integer greater than or equal to 1), and a main crankshaft having an eccentric hub shaft supporting the rotor; a transmission gear installed between a curved rotor and a main crankshaft, the transmission gear comprising: (a) an internal ring gear fixed or fixed to one side of the curved rotor; and (b) the main crankshaft. a first cluster gear having a hollow shaft that freely rotates by a roller bearing within the crankshaft, and comprising a small gear that acts as a pinion gear with respect to the internal ring gear, and a large gear that meshes with a second cluster gear device; (c) a second cluster gear having a separate rerank shaft and comprising a small gear meshing with a large gear of the first cluster gear device and a large gear meshing with a final pinion gear fixed within the main crankshaft; (d) consists of a final pinion gear that is fixed or fixed to the main crankshaft and is captured; (e) for a 2-apex type rotor, the gear ratio between the internal ring gear and the pinion is 3:2; for a 3-apex type rotor, the internal The gear ratio between the ring gear and the pinion is 4:3, the gear ratio between the internal ring gear and the pinion is 5:4 in the 4-apex type rotor, and the meshing gear ratio is 1: in the (f) 2-apex type rotor.
2 and 1:2, 3-apex rotors have meshing gear ratios of 1:3 and 1:3, and 4-apex rotors have meshing gear ratios of 1:4 and 1:4 (smaller ratios are (with respect to small gears, large ratios with respect to large gears) rotary machines. 2. The rotary machine according to claim 1, wherein the rotary machine is a rotary internal combustion engine. 3. The rotary machine according to claim 1, wherein the rotary machine is a rotary pump. 4. The rotary machine according to claim 1, wherein the rotary machine is a rotary compressor. 5. The rotary machine according to claim 1, wherein the internal ring gear is fixed with bolts and nuts. 6. The rotary machine according to claim 1, wherein the final pinion gear is fixed with an involute spline and reinforced with a special lock nut. 7. A rotary machine according to claim 1, having a rotor with a flat outer surface and a housing cavity parallel to the axial shaft instead of a radially curved rotor and a radially arcuate housing cavity. 8. The rotary machine according to claim 1 or 7,
Instead of a meshing gear between the rotor and the main crankshaft, a planetary or epicyclic gearing is provided, whereby the pinion gear is made integrally within the cluster arm and the gearing and within the main crankshaft. The arm is equipped with three arm shafts that hold three units of rotatable planetary gears that mesh with the sun gear as well as the outer ring gear; (a) The outer ring gear is fixed within the outer part of the housing frame, whereas the sun gear is fixed or fixed to the main crankshaft and reinforced; (b) In rotary machines with two-apex rotors, the inner ring gear and pinion When the gear ratio is fixed at 3:2, the gear ratio of the outer ring gear, planet gear, and sun gear is 3:1:1, and (c) In a rotary machine with a 3-apex rotor, the planet gear is It is provided in a cluster gear device and consists of a small gear and a large gear.The large gear meshes with the sun gear, while the small gear meshes with the outer ring gear, and the gear ratio between the internal ring gear and pinion is fixed at 4:3. The gear ratio between the outer ring and the small gear of the planet gear is 4:1, and the gear ratio between the large gear of the planet gear and the sun gear is 2:1, and (d) a rotary with a 4-apex type rotor. The machine has the same configuration as above, and when the gear ratio of the inner ring gear and pinion is fixed at 5:4, the gear ratio of the outer ring gear and the small gear of the planet gear is 5:1, and the planet gear A rotary machine configured so that the gear ratio between the large gear and the sun gear is 3:1. 9 the outer ring gear is fixed with bolts and nuts;
9. The rotary machine according to claim 8, wherein said sun gear is fixed with an involute spline and reinforced with a special lock nut. 10 In order to obtain a wide range of gear combinations required under various conditions, the required transmission devices based on different gear ratios are ▲mathematical formulas, chemical formulas, tables, etc.▼ (However, I.I.G.P. .: Internal involute gear pinion, I.I.G.: Internal involute gear, a
/b: additional revolution of the internal involute gear per revolution of the main crankshaft, P: the basic ratio of each particular type of rotary machine, epicyclic, two-lobed epitrochoidal and three-lobed epitrochoidal housing cavity. 9. The rotary machine according to claim 8, wherein the rotary machine is manufactured based on the formula: 1/2, 2/3 and 3/4 for each part. 11. The transmission device according to claim 10, wherein the internal involute gear pinion rotates in the same direction as the main crankshaft when the a/b quotient is positive, and in the opposite direction when the quotient is negative. rotary machine. 12. Rotary machine according to claim 11, comprising a 3-apex rotor and a 6-lobed outer surface with a curved or flat surface. 13. The rotary machine of claim 12, wherein the outer portion of the housing is provided with ports for inlet and outlet passages communicating with the working chamber. 14 The outer portion of the housing is provided with ports for inlet and outlet passages communicating with the working chamber, including valves, a combustion system using some fuel and using spark plugs or fuel injectors, some cooling system, and some quality lubricating oil. 13. A rotary machine as claimed in claim 12, further comprising sealing elements between the cooperating parts and the like. 15. The transmission device has one or more gears suitable for the above-mentioned principles and is fixed or installed on the main crankshaft and other associated parts that may or may not be in mesh with each other, so that the outer envelope of the rotating rotor can be controlled with precise timing. 15. The rotary machine of claim 14, wherein rotation of the rotor and main crankshaft is maintained according to a predetermined ratio so as to form the desired shape at the appropriate speed ratio. 16. The rotary machine of claim 15, wherein the gear is an involute. 17. The rotary machine of claim 15, wherein the gear is hypoid. 18. Any engine or rotary machine or rotary machine using any fuel, suitable for use as land, sea or air transport, aircraft engine or other flying vehicle, using the aforesaid principles, or special cutting. Claims 1, 2, 3, including all kinds of vehicles, equipment or devices equipped with a device, rotary compressor, rotary pump or other rotary device.
4, 5, 6, 7, 8, 9, 10, 11, 12, 13, 1
4, 15, 16 or 17.