DE102011089609A1 - Internal gear pump - Google Patents

Abstract

Internal-gear pump for delivering a fluid, comprising an internal gearwheel (22) with an internal toothed ring, an external gearwheel (24) with an external toothed ring, wherein the teeth (21) of the internal and external gearwheel (22, 24) engage into one another and the internal gearwheel (22) or the external gearwheel (24) is driven, a working chamber (47) which is formed between the internal gearwheel (22) and the external gearwheel (24) and is divided into an inflow working chamber (30) and into an outflow working chamber (31), an inflow channel (28) which opens into the inflow working space (30) for introducing the fluid to be delivered into the inflow working chamber (30), and an outflow channel (29) which opens into the outflow working chamber (31) for discharging the fluid to be delivered out of the outflow working chamber (31), the teeth (21) of the internal gearwheel (22) and the teeth (21) of the external gearwheel (24) in each case have a drive flank (51) and a free flank (52) which lies opposite the drive flank (51), and the drive flanks (51) of the internal and external gearwheel (22, 24) lie on one another in order to transmit a torque from the driven gearwheel (22, 24) to the non-driven gearwheel (22, 24), wherein the geometry of the drive flanks (51) of the internal and/or external gearwheel (22, 24) is configured in such a way that at least two teeth (21) of the internal and external gearwheel (22, 24) lie on one another and, at the tip point (48), there is a spacing or a play between the teeth (21) of the internal gearwheel (22) and the teeth (21) of the external gearwheel (24).

Description

The present invention relates to an internal gear pump according to the preamble of claim 1 and a high-pressure injection system according to the preamble of claim 12.

State of the art

Internal gear pumps or gerotor pumps have an internal gear and an external gear. The teeth of the inner and outer gear engage with each other and between the inner and outer gear forms a working space. In this case, the working space is subdivided into an inflow work space and into an outflow work space. The inflow working space thus constitutes a suction side and the outflow working space constitutes a pressure side of the internal gear pump. An inflow channel opens into the inflow working space and an outflow channel opens into the outflow working space. In this case, a gear is driven and at a contact point of a tooth of the inner and outer gear torque is transmitted from the driven gear to the non-driven gear. At this contact point are drive flanks of the two teeth in contact with each other.

Opposite a Kämmstelle a headend between the inner and outer gear is present. At the headend, no torque is transmitted from the outer gear to the inner gear, and leakage losses occur between the inflow work space and the outflow work space, that is, leakage. H. the pressurized fluid flows from the effluent working space into the inflow working space. To compensate for manufacturing inaccuracies and thermal deformations a game between the inner and outer gear is present at the head end and it thereby occurs leakage.

Furthermore, it is known, according to the so-called "Eckerle-principle" to put the teeth of the inner and outer gear in the region of the head end under a compressive bias. Although this leakage losses at the head end can be avoided or they can be reduced, however, there is a greater wear on the teeth of the inner and outer gear and it increase the mechanical friction losses at the head end strongly, which in turn reduces the efficiency of the internal gear pump or Energy losses increased.

It is theoretically possible due to mathematical calculations to construct the inner and outer gears so that all the teeth of the internal gear with all teeth of the external gear are in contact, so that there would be no leakage. In this case, for example, the teeth of the external gear are given in a section perpendicular to a rotation axis of the external gear as circle segments and depending on the geometry of the teeth of the external gear, the teeth of the internal gear are constructed. This is, for example, in the diploma or master's thesis on the subject Boris Mathieu from 14.02.2005 to 12.08.2005 at the Ecole supérieur des sciences et technologies de l'engineer de Nancy 2, rue Jean Lamour, 54519 Vandoeuvre les Nancy Cedex in. "Modeling and study of a new pump concept for braking systems" France described. However, such gear pumps can not be built in practice, because due to manufacturing inaccuracies and thermal deformations assembly would not be possible and also would occur in operation very large pressure biases and friction losses between the teeth of the inner and outer gear.

From the DE 36 24 532 C2 For example, there is known a vane or internal gear pump having a plurality of sealed delivery cells whose volume changes from a minimum to a maximum value and back during one revolution. The pump is used in particular for fuel delivery of an internal combustion engine. With axially entering into the feed cells suction and pressure channels, the mouth cross-sections are designed for a promotion without internal compression, however, such is created by against axial surfaces of the pump parts applied, check valves forming fixed thrust washers.

From the DE 34 06 349 A1 a displacement machine with at least two gear machines is known, which is assigned a separate or common hydraulic circuit, and their common flow is variable by a control means, wherein the control means is arranged in a housing part of the positive displacement machine.

The DE 299 13 367 U1 shows an internal gear pump with at least one internally toothed ring gear and a meshing, externally toothed impeller, with or without sickle, and with an electric drive, which is formed by the ring gear disposed inside a rotor of a brushless electric motor and the rotor adjacent to a stator is, wherein the rotor containing the ring gear is rotatably supported on the outside by a bearing or a sliding bearing, wherein the stator is shielded and sealed relative to the rotor and the interior of the pump characterized in that the located between the stator and rotor bearings or bearings for liquid impermeable and is tightly connected at its two end faces in each case with a cover.

Disclosure of the invention

Advantages of the invention

Internal gear pump according to the invention, in particular for a motor vehicle, for conveying a fluid, comprising an internal gear with an internal gear, an external gear with an external gear, wherein the teeth of the internal and external gear mesh and the internal gear or the external gear is driven, one between the internal gear and the outer gear formed working space, which is divided into a Zuströmarbeitsraum and in a Abströmarbeitsraum, an opening into the Zuströmarbeitsraum inflow channel for introducing the fluid to be conveyed in the Zuströmarbeitsraum and opening into the Abströmarbeitsraum outflow channel for diverting the fluid to be delivered from the Abströmarbeitsraum, preferably the inflow working space and the outflow working space are separated from each other at a head position and at a meshing point between the internal and external gears, the teeth of the internal gear and the teeth of the external gear, respectively Have a drive edge and the drive edge opposite free edge and the drive flanks of the inner and outer gear to each other for transmitting torque from the driven gear to the non-driven gear, wherein the geometry of the drive flanks of the inner and / or outer gear are formed such that at least two teeth of the inner and outer gears lie on each other and at the head end there is a clearance or a clearance between the teeth of the internal gear and the teeth of the external gear. In an advantageous manner occurs on a plurality of teeth of the inner and outer gear contact, so that on the one hand in this area of the inflow or Abströmarbeitsraumes in which the teeth on the drive flanks face each other or contact have no leaks occur and on the other hand is at the Headend and in the vicinity of the headend between the teeth of the inner and outer gear clearance or a distance, so that thereby an assembly of the inner and outer gear is possible and no or very little pressure biases and friction losses between the teeth of the inner and External gear occur

In an additional embodiment, the geometry of the free flanks of the inner and / or outer gear is formed to the effect that the teeth of the inner and outer gear have a clearance or clearance on the free flanks. As a result, substantially no frictional forces or pressure biases occur at the free flanks, and the compressive biases on the drive flanks are substantially low and the compressive biases essentially correspond only to the required compressive force for transmitting the torque from the driven gear to the non-driven gear.

In a further variant, the teeth of the internal gear and the teeth of the external gear on a tooth head and the geometry of the tooth tips of the inner and / or outer gear are designed such that the tooth tips of the teeth of the internal gear no contact with the teeth, in particular the tooth tips and have the free edges of the teeth, the external gear and / or the tooth tips of the teeth of the external gear have no contact with the teeth, in particular the tooth tips and the free edges of the teeth of the internal gear on. In this way, essentially no pressure biases and frictional forces occur at the tooth tips, in particular at the head end.

Suitably, the tooth tips of the teeth of the inner and outer gears comprise the last 30%, 20% or 10% of the radial extent of the teeth of the inner and outer gears towards an axis of rotation of the respective gear and preferably the drive flanks and / or the flanks are outside formed the tooth tips of the teeth of the inner and outer gear.

In a supplementary variant, the distance or play between the teeth of the inner and outer gear at the head end and / or at the free flanks of the teeth of the inner and outer gear is at least 5 .mu.m, 10 .mu.m, 20 .mu.m, 40 .mu.m or 60 .mu.m and / or less than 200, 150, 100 or 80 microns and / or between 10 .mu.m and 150 .mu.m, in particular between 20 .mu.m and 100 .mu.m. A clearance or clearance of this magnitude is required to avoid manufacturing inaccuracies and thermal deformations. to be able to compensate.

In an additional embodiment, the geometry of the drive flanks of the inner and / or outer gear is designed such that at least three, four or five teeth of the inner and outer gear lie on each other. As a result, leakages do not occur in a large area of the inflow or outflow working space.

Suitably, the internal gear pump is a gerotor pump. In a further embodiment, the internal gear pump comprises an electric motor with a stator and a rotor and the driven gear is formed by the rotor.

In a supplementary embodiment, permanent magnets of the rotor are installed or integrated in the driven gear.

Suitably, the stator is concentric with the rotor. In a further embodiment, the external or internal gear is formed by the rotor.

In particular, permanent magnets of the rotor are installed or integrated in the external or internal gear.

In a further embodiment, the inflow channel opens only partially into an inflow workspace with an increasing volume, and the outflow duct discharges into an outflow working space with a decreasing volume and additionally in part into the inflow workspace.

In an additional variant, the inflow angle range is equal to or greater than the pressure angle range and the outflow angle range is greater than 180 ° such that there is no contact point at a seal angle range and preferably all contact points are present at the inflow angle range or the inflow angle range is less than the pressure angle range and the outflow angle range is greater than 180 °, so that there is a contact point at the sealing angle range. If no contact point exists at the sealing angle range between the inflow angle range and the outflow angle range, a slight leakage occurs between the inflow and outflow channel due to the small clearance or the small distance. At this time, the clearance or the distance from the last contact point toward the headend on the teeth increases toward the headend. For example, if the first tooth is present after the last tooth in the direction of the head end at the sealing angle range, due to the small clearance or the small distance only a small leakage occurs. If there is a contact point at the sealing angle range, essentially no leakage occurs between the inflow and outflow channel, because an essentially complete sealing is ensured at the contact point due to the contact.

In an additional embodiment, the outflow channel only partially opens into a downstream working space with a decreasing volume and the inflow channel opens into an inflow working space with an increasing volume and additionally in part into the outflow working space.

In a further refinement, the outflow angle range is equal to or greater than the pressure angle range and the inflow angle range is greater than 180 °, so that no contact point is present at a sealing angle range and preferably all contact points are present at the outflow angle range or the outflow angle range is smaller than the pressure angle range and the inflow angle range is greater than 180 °, so that a contact point is present at the sealing angle range.

In a supplementary variant, the pressure angle range starts at a driven inner gear in the direction of the Kämmstelle and a driven outer gear opposite to the direction at the Kämmstelle.

The tooth expediently has only one contact point at the combing point. In a further embodiment, the inflow angle range and the outflow angle range start in the opposite direction at the combing point and preferably the inflow angle range at the end of the inflow duct and the outflow angle range preferably ends at the end of the inflow duct or, deviating from this, the inflow angle range is present only at the inflow duct and the outflow angle range is only on the outflow channel available.

Inventive high-pressure injection system for an internal combustion engine, in particular for a motor vehicle, comprising a high-pressure pump, a high-pressure rail, a, preferably electric, prefeed pump for conveying a fuel from a fuel tank to the high-pressure pump, wherein the prefeed pump is designed as a prefeed pump described in this patent application.

In a variant, the internal gear and the external gear are mounted eccentrically to each other.

Suitably, the pump with, preferably integrated, electric motor comprises a, preferably electronic, control unit for controlling the energization of the electromagnets and / or the electric motor of the pump is an electronically commutated electric motor.

Suitably consists of the housing of the prefeed pump and / or the housing of the high-pressure pump and / or the inner and / or outer gear at least partially, in particular completely, made of metal, for. As steel or aluminum.

The pressure angle range preferably corresponds to the extent of the inflow or outflow channel.

In particular, the delivery rate of the electrical feed pump can be controlled and / or regulated.

Brief description of the drawings

Hereinafter, embodiments of the invention will be described in more detail with reference to the accompanying drawings. It shows:

1 a highly schematic view of a high-pressure injection system,

2 a perspective view of an internal gear pump without a housing and a stator,

3 an exploded view of the internal gear pump according to 2 .

4 a cross section of the internal gear pump according to 2 are integrated in the permanent magnet in the internal gear,

5 a cross section of the internal gear pump according to 2 are integrated in the permanent magnet in the internal gear, wherein the inflow and outflow channel is designed differently,

6 a detailed view of a headend of the internal gear pump according to 4 and 5 ,

Embodiments of the invention

In 1 is a pump arrangement 1 a high pressure injection system 2 represented for a motor vehicle, not shown. An electric feed pump 3 promotes from a fuel tank 41 through a fuel line 35 Fuel. Subsequently, the fuel from the electric feed pump 3 to a high pressure pump 7 promoted. The high pressure pump 7 is from an internal combustion engine 39 by means of a drive shaft 44 driven.

The electric prefeed pump 3 has an electric motor 4 and a pump 5 on ( 2 and 3 ). Here is the electric motor 4 the pump 5 into the pump 5 integrated and also is the electric feed pump 3 at the high pressure pump 7 arranged directly (not shown). The high pressure pump 7 Promotes fuel under high pressure, for example, a pressure of 1000, 3000 or 4000 bar, through a high-pressure fuel line 36 to a high-pressure rail 42 , From the high-pressure rail 42 The fuel is under high pressure from an injector 43 a combustion chamber, not shown, of the internal combustion engine 39 fed. The non-combustion fuel is supplied by a return fuel line 37 back to the fuel tank 41 recycled. An inflow channel 28 ( 3 and 4 ) of the electrical feed pump 3 sucks fuel through a fuel line 35 from a fuel tank 41 on and through a discharge channel 29 the fuel gets through the fuel line 35 the high pressure pump 7 fed.

In the fuel line 35 from the fuel tank 41 to the electric feed pump 3 is a fuel filter 38 built-in. This can advantageously the fuel line 35 from the fuel tank 41 to the electric feed pump 3 be formed inexpensively, since they must withstand any overpressure. The electric motor 4 ( 3 and 4 ) of the electrical feed pump 3 is operated with three-phase current or alternating current and is controllable in power and / or regulated. The three-phase current or alternating current for the electric motor 4 is from a power electronics, not shown, from a DC voltage network of a vehicle electrical system of a motor vehicle 40 made available. The electric prefeed pump 3 is thus an electronically co-fed prefeed pump 3 ,

The electric prefeed pump 3 has a housing 8th with a housing pot 10 and a housing cover 9 on ( 3 ). Inside the case 8th the pre-feed pump 3 are the pump 5 as internal gear pump 6 or gerotor pump 26 and the electric motor 4 arranged. The housing pot 10 is with a recess 54 Mistake. The electric motor 4 has a stator 13 with windings 14 as electromagnets 15 and a soft iron core 45 as a soft magnetic core 32 on that as a laminated core 33 is trained. Inside the stator 13 is the pump 5 as internal gear pump 6 with an internal gear 22 with an internal toothed ring 23 and an external gear 24 with an external tooth ring 25 positioned. The internal and external gear 22 . 24 makes a gear 20 and an impeller 18 and the inner and outer teeth ring 23 . 25 have teeth 21 as conveying elements 19 on. Between the inner and outer gear 22 . 24 a working room is formed 47 out. In the external gear 24 are permanent magnets 17 fitted so that the external gear 24 also a rotor 16 of the electric motor 4 forms. The electric motor 4 is in the pump 5 integrated or vice versa. The electromagnets 15 of the stator 13 are alternately energized, so that due to the contact with the electromagnet 15 resulting magnetic field of the rotor 16 or the external gear 24 in a rotational movement about a rotation axis 27 respectively. 27 b is shifted.

The housing cover 9 serves as a warehouse 11 or thrust bearing 11 or slide bearing 11 for the internal or external gear 22 . 24 , Furthermore, in the housing cover 9 the inflow channel 28 and the discharge channel 29 incorporated. By inflow channel 28 the fluid to be pumped, namely fuel, flows into the prefeed pump 3 in and out of the discharge channel 29 the fuel flows out of the prefeed pump again 3 out. In addition, the housing pot 9 and the housing cover 10 three holes each 46 on, in which screws, not shown, for screwing together the housing pot 9 and the housing cover 10 are positioned, with one not illustrated seal the housing pot 9 and the housing cover 10 lie fluid-tight on each other.

The internal gear pump 6 or the gerotor pump 26 has a workspace 47 on. The workroom 47 is doing so in a Zuströmarbeitsraum 30 as a suction side and a Abströmarbeitsraum 31 divided as printed page ( 4 ). At the inflow workroom 30 increases the working space 47 and at the downstream working space 31 the working space is reduced 47 ie delivery areas between the teeth 21 of the internal and external gear 22 . 24 , The angular range of the inflow working space and the angular range of the outflow working space are in each case 180 °.

In the in 4 illustrated internal gear pump 6 is different from 2 and 3 not the external gear 24 but the internal gear 22 the driven gear 22 ie the permanent magnets 17 are in the internal gear 22 built-in or integrated and the internal gear 22 forms the rotor 16 of the electric motor 4 , The internal and external gear 22 . 24 is in one direction 34 driven. The internal and external gear 22 . 24 are eccentric to each other with an eccentricity e. This leads the internal gear 22 a rotational movement about the axis of rotation 27a off and the outside gear 24 performs a rotational movement about the axis of rotation 27 b and the two rotation axes 27a and 27 b have the distance e. The external gear 24 indicates at the extreme inner point of a tooth head 50 the radius R _az on and between the teeth 21 at the lowest point the radius R _am . The difference between R _az and R _am thus corresponds to the radial extent of the teeth 21 of the external gear 24 , In 5 is the tooth head 50 by a horizontal dashed line from the outer tooth 21 separated. The tooth head 50 on the teeth 21 of the external gear 24 thus takes about the last 30% of the radial extent of the teeth 21 towards the axis of rotation 27 b of the external gear 24 one. In an analogous way, the teeth 21 of the internal gear 22 at the outermost point of the tooth head 50 the radius R _iz on and between the teeth 21 at the lowest point the radius R _in .

In 4 is a section perpendicular to the axes of rotation 27a . 27b shown. The teeth 21 of the external gear 24 are on the outside as a circle segments formed with a circle with the center M and the radius S ( 5 ). Where K is the distance from M to the axis of rotation 27b of the external gear 24 , The geometry of the teeth 21 of the internal gear 22 is dependent on the geometry of the teeth 21 of the external gear 24 constructed as a cycloid according to the diploma or master thesis on the subject Boris Mathieu from 14.02.2005 to 12.08.2005 at the Ecole supérieur des sciences et technologies de l'engineer de Nancy 2, rue Jean Lamour, 54519 Vandoeuvre les Nancy Cedex in. "Modeling and study of a new pump concept for braking systems" France , In this construction or mathematical calculation of the teeth 21 of the internal gear 22 become the actual radius S of the teeth 21 of the external gear 24 and a fictitious radius S _f used with the notional radius S _f is greater than the actual radius S. The teeth 21 of the external gear 24 thus in fact have exclusively the radius S, which in 5 is shown by a solid line. The notional radius S _f and a transition region 53 are shown with a dashed line. The fictitious radius S _f on the teeth 21 of the external gear 24 occurs outside the drive flanks 51 the teeth 21 of the external gear 24 on and in a steady transition area 53 the fictitious radius S _{f is} adapted to the radius S. At the teeth heads 50 and on the free flanks 52 Thus, the fictitious radius S _{f is} present. At the drive flanks 51 is the radius S available. The geometry of the teeth 21 of the internal gear 22 is at the drive flanks 51 depending on the radius S designed or calculated and on the free flanks 52 as well as the tooth heads 50 depending on the notional radius S _f . The transition area 53 also occurs on the teeth 21 of the internal gear 22 on. The solid line in 5 represents the actual tooth 21 of the internal gear 22 dar. The solid line on the drive edge 51 was constructed as a function of the actual radius S and the solid line on the tooth tip 50 and the free flank 52 was constructed as a function of the notional radius S _f . The dashed line on the tooth head 50 and on the free flank 52 of the tooth 21 of the internal gear 22 were constructed depending on the actual radius S. The transition area 53 thus occurs on the internal gear 22 on the solid line on. This is in 5 a game or a gap between the tooth 21 of the internal gear 22 and the tooth 21 of the external gear 24 present, which in 4 not shown. This occurs between the teeth 21 of the internal and external gear 22 . 24 between the teeth heads 50 and the free flanks 52 a game or a gap in 4 not shown. Only at the drive edges 51 exists at three contact points 40 a contact between the teeth 21 of the internal and external gear 22 . 24 to a torque from the internal gear 22 on the external gear 24 because of the geometry of the teeth 21 of the internal gear 22 on the drive flanks 51 according to the actual radius S of the teeth 21 of the external gear 24 constructed or calculated. In 4 are only contact points 40 shown; due to the spatial extent of the internal and external gear 22 . 24 perpendicular to the plane of the drawing are the contact points 40 but actually contact lines. Thereby it comes at an engagement angle range α _K with the contact points 40 essentially not to leaks or flow losses between the delivery chambers between the teeth 21 of the internal and external gear 22 . 24 because the drive flanks 51 the teeth 21 of the internal and external gear 22 . 24 lie on each other under a compressive force due to the transmission of torque from the internal gear 22 on the external gear 24 , The pressure angle range expediently corresponds to the extent of the inflow channel 28 (not shown). The inflow channel 28 is present at an inflow channel angle range α _Z and the inflow channel angle range α _Z begins counterclockwise at the combing point 49 and ends at the end of the inflow channel 28 in the area of the headend 48 , so that the inflow channel angle range α _{Z has} an angle of approximately 170 °. The pressure angle range α _K with the contact points 40 also starts counterclockwise at the combing point 49 and ends at the last of the three contact points 40 such that the pressure angle range α _{K is} approximately 70 °. The discharge channel 29 is present at a Abströmkanalwinkelbereich α _A and the Abströmkanalwinkelbereich α _A begins clockwise at the Kämmstelle 49 , so that the outflow channel angle range α _{A has} an angle of about 170 °. A sealing angle range α _D is in the area of the head end 48 between the inflow angle range α _Z and the outflow angle range α _A present. Due to the large distance or clearance between the teeth 21 in the area of the headend 48 thus occur large leakage losses between the inlet and outlet channel 28 . 29 on.

In a further, not shown embodiment is not the internal gear 22 but the external gear 24 driven. The contact points 40 This does not occur counterclockwise starting at the combing point 49 on, but in a clockwise direction starting at the Kämmstelle 49 , The drive flanks 51 occur on the teeth 21 opposite compared to the teeth 21 in 4 and 5 on. Appropriately corresponds in this embodiment, not shown, the pressure angle range of the expansion of the outflow channel 29 (not shown).

In 5 is another embodiment of the internal gear pump 6 shown and in the following essentially only the differences from the embodiment according to 4 described. The inflow channel 28 is only in the range of the contact points 40 trained and there are four contact points 40 present, one of which is a contact point 40 outside the inflow channel 28 is present at the sealing angle range α _D and in addition, the discharge channel 29 not only at the workroom or workrooms with a decreasing volume, ie the in 5 right of the head and Kämmstelle 48 . 49 available, but also partially to the work space 47 or work rooms as Zuströmarbeitsraum 30 with an increasing volume, ie the in 5 left of the head and Kämmstelle 48 . 49 available. This will only have two working spaces between the teeth 21 with the contact points 40 used as a working space for conveying fluid. Essentially there are no leakage losses between the inflow and outflow ducts 28 . 29 on, because at the sealing angle range α _D , ie the area between the inlet and outlet channel 28 . 29 , a contact point 40 is present at the due to the contact a substantially complete seal is ensured. The game or the distance between the teeth 21 takes out of the pressure angle range α _K counterclockwise at the delivery chambers with the increasing volume towards the headend 48 to. Would be the inflow channel 28 contrary to the illustration in 5 slightly towards the headend 48 over the last contact point 40 extended and the outflow channel 29 Correspondingly shortened, a slight leakage would occur and there could be three working spaces between the teeth 21 be used to convey the fluid. A slight leakage with an increased number of delivery spaces between the teeth for conveying the fluid could be useful to the flow rate of the pump 5 to increase.

Overall, are considered with the internal gear pump according to the invention 6 significant benefits. Due to the game or the distance to the teeth heads 50 and the free flanks 52 the friction losses are very low and the increased number of contact points 40 lowers the contact pressure at the contact points 40 and thus also the wear.

QUOTES INCLUDE IN THE DESCRIPTION

This list of the documents listed by the applicant has been generated automatically and is included solely for the better information of the reader. The list is not part of the German patent or utility model application. The DPMA assumes no liability for any errors or omissions.

Cited patent literature

• DE 3624532 C2 [0006]
• DE 3406349 A1 [0007]
• DE 29913367 U1 [0008]

Cited non-patent literature

• Boris Mathieu from 14.02.2005 to 12.08.2005 at the Ecole supérieur des sciences et technologies de l'engineer de Nancy 2, rue Jean Lamour, 54519 Vandoeuvre les Nancy Cedex in. "Modeling and study of a new pump concept for braking systems" France [0005]
• Boris Mathieu from 14.02.2005 to 12.08.2005 at the Ecole supérieur des sciences et technologies de l'engineer de Nancy 2, rue Jean Lamour, 54519 Vandoeuvre les Nancy Cedex in. "Modeling and study of a new pump concept for braking systems" France [0045]

Claims (14)

Internal gear pump ( 6 ) for conveying a fluid, comprising - an internal gear ( 22 ) with an internal toothed ring ( 23 ), - an external gear ( 24 ) with an external toothed ring ( 25 ), - whereby the teeth ( 21 ) of the inner and outer gear ( 22 . 24 ) and the internal gear ( 22 ) or the external gear ( 24 ), - one between the internal gear ( 22 ) and the external gear ( 24 ) trained working space ( 47 ) entering an inflow workspace ( 30 ) and in a downstream working space ( 31 ), - one in the Zuströmarbeitsraum ( 30 ) inflowing inflow channel ( 28 ) for introducing the fluid to be conveyed into the inflow work space ( 30 ) and one in the Abströmarbeitsraum ( 31 ) discharging outflow channel ( 29 ) for diverting the fluid to be delivered from the Abströmarbeitsraum ( 31 ), - the teeth ( 21 ) of the internal gear ( 22 ) and the teeth ( 21 ) of the external gear ( 24 ) each have a drive edge ( 51 ) and one of the drive flank ( 51 ) opposite free flank ( 52 ) and the drive edges ( 51 ) of the inner and outer gear ( 22 . 24 ) lie on each other for transmitting a torque from the driven gear ( 22 . 24 ) on the non-driven gear ( 22 . 24 ), characterized in that the geometry of the drive flanks ( 51 ) of the inner and / or outer gear ( 22 . 24 ) are formed such that at least two teeth ( 21 ) of the inner and outer gear ( 22 . 24 ) and at the headend ( 48 ) a distance or a play between the teeth ( 21 ) of the internal gear ( 22 ) and the teeth ( 21 ) of the external gear ( 24 ) consists. Internal gear pump according to claim 1, characterized in that the geometry of the free flanks ( 52 ) of the inner and / or outer gear ( 22 . 24 ) are formed so that the teeth ( 21 ) of the inner and outer gear ( 22 . 24 ) a clearance or clearance on the free flanks ( 52 ) exhibit. Internal gear pump according to claim 1 or 2, characterized in that the teeth ( 21 ) of the internal gear ( 22 ) and the teeth ( 21 ) of the external gear ( 24 ) a tooth head ( 50 ) and the geometry of the tooth heads ( 50 ) of the inner and / or outer gear ( 22 . 24 ) are formed so that the tooth heads ( 50 ) the teeth ( 21 ) of the internal gear ( 22 ) no contact with the teeth ( 21 ), in particular the tooth heads ( 50 ) and the free flanks ( 2 ) the teeth ( 21 ), the external gear ( 24 ) and / or the tooth heads ( 50 ) the teeth ( 21 ) of the external gear ( 24 ) no contact with the teeth ( 21 ), in particular the tooth heads ( 50 ) and the free flanks ( 2 ) the teeth ( 21 ), of the internal gear ( 22 ) exhibit. Internal gear pump according to claim 3, characterized in that the tooth heads ( 50 ) the teeth ( 21 ) of the inner and outer gear ( 22 . 24 ) the last 30%, 20% or 10% of the radial extent of the teeth ( 21 ) of the inner and outer gear ( 22 . 24 ) in the direction of a rotation axis ( 27a . 27b ) of the respective gear ( 22 . 24 ) and preferably the drive flanks ( 51 ) and / or the free flanks ( 52 ) outside the tooth heads ( 50 ) the teeth ( 21 ) of the inner and outer gear ( 22 . 24 ) are formed. Internal gear pump according to one or more of the preceding claims, characterized in that the distance or play between the teeth ( 21 ) of the inner and outer gear ( 22 . 24 ) at the headend ( 48 ) and / or on the free flanks ( 52 ) the teeth ( 21 ) of the inner and outer gear ( 22 . 24 ) is at least 5 μm, 10 μm, 20 μm, 40 μm or 60 μm and / or less than 200 μm, 150 μm, 100 μm or 80 μm and / or between 10 μm and 150 μm, in particular between 20 μm and 100 μm lies. Internal gear pump according to one or more of the preceding claims, characterized in that the geometry of the drive flanks ( 51 ) of the inner and / or outer gear ( 22 . 24 ) in that at least three, four or five teeth ( 21 ) of the inner and outer gear ( 22 . 24 ) lie on one another. Internal gear pump according to one or more of the preceding claims, characterized in that the internal gear pump ( 6 ) a gerotor pump ( 26 ). Internal gear pump according to one or more of the preceding claims, characterized in that the internal gear pump ( 6 ) an electric motor ( 4 ) with a stator ( 13 ) and a rotor ( 16 ) and the driven gear ( 22 . 24 ) through the rotor ( 16 ) is formed. Internal gear pump according to claim 8, characterized in that in the driven gear ( 22 . 24 ) Permanent magnets ( 17 ) of the rotor ( 16 ) are installed or integrated. Internal gear pump according to one or more of the preceding claims, characterized in that the inflow channel ( 28 ) only partially into an inflow workspace ( 30 ) opens with an increasing volume and the outflow channel ( 29 ) into a downstream working space ( 31 ) with a decreasing volume and in addition partially in the Zuströmarbeitsraum ( 30 ) opens. Internal gear pump according to claim 10, characterized in that the inflow angle range is equal to or greater than the pressure angle range and the outflow angle range is greater than 180 °, so that at a sealing angle range no contact point ( 40 ) and preferably all contact points ( 40 ) are present at the inflow angle range or the inflow angle range is smaller than the pressure angle range and the outflow angle range is greater than 180 °, so that at the sealing angle range a contact point ( 40 ) is available. Internal gear pump according to one or more of claims 1 to 9, characterized in that the outflow channel ( 29 ) only partially into a Abströmarbeitsraum ( 31 ) opens with a decreasing volume and the inflow channel ( 28 ) into an inflow workspace ( 31 ) with an increasing volume and in addition partially into the Abströmarbeitsraum ( 31 ) opens. Internal gear pump according to claim 12, characterized in that the outflow angle range is equal to or greater than the pressure angle range and the inflow angle range is greater than 180 °, so that at a sealing angle range no contact point ( 40 ) and preferably all contact points ( 40 ) are present at the outflow angle range or the outflow angle range is smaller than the pressure angle range and the inflow angle range is greater than 180 °, so that at the sealing angle range a contact point ( 40 ) is available. High-pressure injection system ( 2 ) for an internal combustion engine ( 39 ), comprising - a high-pressure pump ( 7 ), - a high-pressure rail ( 42 ), - one, preferably electric, feed pump ( 3 ) for conveying a fuel from a fuel tank ( 41 ) to the high pressure pump ( 7 ), characterized in that the prefeed pump ( 3 ) is formed according to one or more of the preceding claims.

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