WO2021005151A1

WO2021005151A1 - Pressure supply device with a gear pump

Info

Publication number: WO2021005151A1
Application number: PCT/EP2020/069357
Authority: WO
Inventors: Heinz Leiber; Norbert Alaze
Original assignee: Ipgate Ag
Priority date: 2019-07-10
Filing date: 2020-07-09
Publication date: 2021-01-14
Also published as: DE112020003258A5; DE102019118708A1

Abstract

The invention relates to a pressure supply device with an electromotive drive (21, 23) arranged in a drive housing (18, 22) and a gear pump (Z) which is driven by the electromotive drive, wherein the drive (21, 23) has a stator (23) and a rotor (21), and the gear pump (Z) has a gear (2) coupled to the rotor (21), a wall (18, 40) being arranged between the rotor (21) and the gear (2). The invention is characterized in that at least one seal (13.1) is arranged between the rotor (21) and the gear (2) such that the rotor (21) is a dry-running rotor, around which the medium delivered by the gear (2) does not flow and/or which the medium does not surround.

Description

Pressure supply device with a gear pump

State of the art

Gear pumps or gerotor pumps are widely used for medium to high flow rates. In the pressure range, the gear pump is limited due to the large number of gap seals; in some cases, multi-stage pumps are used in which the pressure load per pump is lower. Gear pumps are mostly used for applications with a pressure of up to 300 bar.

Gear pumps are mostly driven by electric motors. It is widespread here to provide a series connection, i. H. To design the electric motor and pump separately, using a common drive shaft, as disclosed in DE 102017106927 A with a coupling. This requires a lot of installation space, which is particularly disadvantageous when used in a unit with limited space, such as an integrated brake system or a transmission control.

From WO 01/42069 a small motor-pump unit is known in which the pump is essentially arranged within the rotor or the rotor. In this arrangement, however, the size of the pump is limited to the rotor size and the motor mounting and the arrangement of the motor angle sensor is complex. From DE 4113373 a fuel pump for low pressure levels less than 10 bar is known, with mounting of the pump in a kind of flange, but without a connection to a hydraulic block with control valves. In addition, the suction and pressure connections are not located together in the bearing flange. The medium to be pumped flows around the motor, which prevents the pump from being used as a high-pressure pump.

The construction of a gear pump is also made more difficult and complex if it is to act on two hydraulic circuits, as disclosed in WO2012 / 103925, DE 102014212538 and DE 102014117189.

As mentioned at the beginning, the pressure range and also the degree of efficiency depend on the number of sealing surfaces to be sealed, which are dependent, among other things, on the play between the teeth of the intermeshing gears and the play or distance between the inner wall of the housing and the tooth tips that guide along it. It also depends on the tightness between tween the gears and the axially adjacent housing walls. The larger the axial gap between the housing and the gear, the lower the performance and the maximum possible pressure that can be achieved.

The storage of the rotating parts also incurs significant costs. This is problematic, for example, if the motor and pump are designed separately.

Object of the invention

The object of the present invention is to provide a pressure supply device with a gear pump and an integrated electric motor with small dimensions and high efficiency.

solution

The object of the invention is advantageously achieved with a pressure supply device according to claim 1. Advantageous further training of Pressure supply device according to claim 1 result from the features of the subclaims.

The pressure supply device according to the invention is characterized in that it has a motor housing with an electric motor drive arranged in it, which drives a gear pump. The drive has a stator and a rotor for this. An internal gear wheel of the gear pump is moved via the rotor of the drive. The drive is designed according to the invention by means of at least one seal, which is arranged between the rotor and the inner gear wheel, as a dry runner or has a dry running rotor, ie the rotor of the drive is not surrounded by the medium conveyed by the gear pump and / or is not surrounded by the medium. Due to the design as a dry runner, the rotor turns oh ne greater frictional and flow resistances, whereby higher speeds and a better efficiency can be achieved.

A particularly compact and simple pressure supply device is obtained when the motor housing has a side wall on which the gear pump is arranged, in particular this has a recess in which the gear pump is at least partially or completely inserted. The Seitenwan extension of the motor housing can be penetrated by a rotatably connected ver with the rotor shaft, wherein the gear is either rotatably connected to the shaft or is coupled to the shaft via an interposed gear and / or a coupling.

An advantageous compact and integrated design of the pressure supply device described above is obtained when the drive with its housing rests against a hydraulic housing with at least one valve and / or hydraulic lines or channels arranged therein or forms a unit with it. The side wall of the drive housing can abut or abut the side wall of the hydraulic housing, in particular be attached to it, the particularly cup-shaped recess accommodating the gear pump at least partially or completely and being open to the hydraulic housing. In the case of housings arranged next to one another, the gear pump can either be completely in the recess of the wall of the Drive housing, completely in a recess of the hydraulic housing or both in a recess in the side wall of the drive housing and in a recess in the side wall of the hydraulic housing. In the latter case, the openings of the two recesses then face one another. Additional seals can be provided in order to seal the two housings to one another and to the outside.

The above-described recess in the side wall of the drive housing is advantageous to the outside, and if there is a hydraulic housing, open to this. The recess can itself advantageously be designed to be pot-shaped. It can also have a cylindrical section with a circular cross-section in which the gear pump rests with its Zahnrä countries.

The side wall of the drive housing can also advantageously be designed as a flange with which the drive can be attached to another part or unit.

The gear pump used in the pressure supply device according to the invention can be an internal gear pump with a sickle, an external gear pump or a toothed ring pump.

The gear pump can also advantageously be arranged axially next to the stator and / or the rotor of the drive, its structure and size is not disadvantageously limited by the gear pump. The size and structure of the gear pump is then not dependent on the dimensions of the stator and the rotor.

The drive housing can be designed in at least two parts, the side wall being part of a first housing part or forming this. The second housing part can, for example, be cup-shaped and accommodate the stator and the rotor of the drive.

As already stated, the rotor is connected to the gearwheel by means of a drive shaft directly or via a transmission and / or a clutch. The gear can either be by means of a non-positive connection or be non-rotatably connected to the drive shaft by means of a form fit, which is formed in particular by means of a pin or serration. In the gerotor pump, the inner gear is arranged eccentrically on a part connected to the drive shaft, in particular in the form of a disk or a cam disk.

Both in the formation of the gear pump of the pressure supply device according to the invention as an internal gear pump or as a toothed ring pump, an external internal ring gear is also necessary for the internal gear. The internal gear is rotated in the internal gear pump by means of the driven by the drive shaft inner gear about its axis of rotation, the inner gear being arranged eccentrically to the internal gear. The inner ring gear rotates in an outer ring or cylinder surrounding it. In addition, a sickle must be provided, which must be arranged in the space between the inner ring gear and the inner gear wheel resulting from the eccentricity.

In contrast to the internal gear pump, the internal gear ring of the gerotor pump is fixed, the inner gear rolling due to its eccentric mounting on the disc rotated by the drive shaft in the internal gear rim. A sickle as with the internal gear pump is not required.

According to the invention, the drive shaft can either be a) in the motor housing on the one hand and in the gear pump and / or in the hydraulic housing on the other hand or b) only in the gear pump or c) in the hydraulic housing and in the motor housing or d) in the gear pump and in the hydraulic housing or supported by means of suitable Bearings, especially radial bearings, in the form of ball or roller bearings and / or axial bearings.

If a hydraulic housing is provided, the drive shaft can extend up to extend into the hydraulic housing, in particular up to its side opposite the drive. For example, a target for a sensor can be arranged on the drive shaft, the sensor being arranged in the control and regulating unit (ECU). Additional seals can prevent the conveyed medium from entering the control and regulation unit. It is also possible that the drive shaft extends right through the hydraulic housing and ends in the housing adjoining it, for example a control and regulating unit.

The gear pump as an internal gear pump can be designed differently. Thus, in a first embodiment, the inner gear, the inner ring gear, the sickle and the outer ring can be arranged between two disks, with the disks being firmly connected to the outer ring after appropriate centering and adjustment of the parts to one another. Since the material connection can stretch all around the circumference, so that a stable and compact embodiment results in which the individual moving parts only have small games and gaps zueinan of, whereby a good efficiency is achieved and a high one Pressure is achievable.

In a further development of the embodiment described above, the one lateral disk and the outer ring are grouped together to form a cup-shaped part, so that only a material connection between the cup-shaped part and the one disk needs to be established.

Even when the gear pump is designed as a toothed ring pump, the moving parts can be arranged between two disks, which are firmly connected to an outer ring or the inner ring gear. It is also possible to design the outer ring or the inner ring gear with a disk as a component, which in turn is firmly connected to the remaining disk after the remaining parts have been inserted into the cup-shaped part.

In the case of gear pumps with a rotating internal gear rim, a bearing, in particular a ball or roller bearing, can advantageously be placed between the radial outer wall of the internal gear rim and the one encompassing the internal gear rim outer ring or the cylindrical inner wall of the cup-shaped part can be provided in order to keep the friction as small as possible.

The previously described embodiments of the internal gear pumps and gerotor pumps can advantageously be set in a recess in a wall. So that the gear pump rotates in the recess, either a form fit by means of a non-circular shape of the recess and the corresponding contour of the gear pump can be provided or an anti-twist device, e.g. in the form of a bolt, etc. can be provided.

The hydraulic connections for the gear pump can advantageously be provided directly in the wall or recess and / or the at least one disk or the cup-shaped part. This results in a compact design of the pressure supply device according to the invention. Seals can be provided to seal the connections to the channels. This can, for example, lie in the mouth opening of the channel, a groove in a wall running around the channel opening, etc.

In all of the embodiments described above, the internal gear can be arranged tiltably on the shaft. This can be done via a narrow contact surface of the internal gear on the shaft or an elastic connection between the shaft and the internal gear. This allows tolerances to be well balanced, which leads to a smoother running of the gear pump and which advantageously increases the efficiency.

If a hydraulic housing is arranged between the drive housing and the control unit, the electrical connection lines of the electric drive can advantageously be passed through the hydraulic housing through to the housing of the control unit, in particular in at least one channel.

The gear pump can also advantageously be arranged wholly or partly next to the rotor and / or the stator in the axial direction, whereby the stator and / or rotor and also the gear pump can be formed independently of one another. The pressure supply device according to the invention can advantageously serve as a pressure source for a brake system and / or a transmission.

As already stated, the integration of the gear pump into the side wall of the drive housing or the bearing flange of the drive creates a compact structural unit in which a larger structural volume is available for both a single-stage and a two-stage pump.

The mounting can be simplified in that the rotor of the electric motor is mounted only with one bearing arranged in the drive housing and with a second bearing arranged in the gear pump. As described above, however, it is also possible to provide the entire bearing of the rotor in the gear pump. The arrangement can be used for both a brushless motor and a motor with brushes.

The pressure supply device according to the invention can advantageously be used in all systems in which a hydraulic pressure is provided with a pressure supply source and this also has to be regulated, such as in integrated brake systems, transmission controls, robotics, special machines, etc.

As already stated, it is important for efficiency that small gaps are used, which is why a structure with disks and / or pot-shaped parts, internal gear, internal gear, spacer and external rings is chosen so that small tolerances can be maintained , resulting in a closed structural unit in which the parts after adjustment at the outer diameter ßende materially connected to each other, in particular welded, soldered or glued ver.

If only one electric motor is provided in the drive housing, only one hydraulic circuit can be supplied with the pressure supply devices described above. However, it is also within the meaning of the invention that several electric motors are arranged in the drive housing, which drive several gear pumps, the gear pumps being designed as described above, such a pressure supply device being suitable for supplying several hydraulic circuits. Likewise, several single-circuit pressure supply devices according to the invention can be combined can be combined in a module, the module then also being used to supply several hydraulic circuits or units.

In all of the embodiments described above, the gear pumps can be designed both as single-stage and as multi-stage gear pumps, so-called pumps.

It is also possible that with an existing, in particular one-piece, sickle, this can be adjusted or positioned relative to the inner gear within certain limits by means of an adjustment mechanism, so that a certain required play between the inner gear, outer inner toothed ring and sickle can be set taking into account the friction losses is and therefore only a very small leakage occurs from the pressure side to the suction side of the Pum pe. The insertion of the sickle and the setting of the game can be done either manually or automatically.

This adjustment mechanism may be necessary because when assembling the one-piece and the two-piece sickle variant, special measures are taken into account, as neither the sickle nor the gear wheel may have an insertion bevel, as this bevel creates a bypass to the suction side of the pump would. This means that the sickle would have to be positioned very precisely over the narrow gap, which makes automatic assembly of the pump very difficult. Due to the advantageous provision of a corresponding adjustment mechanism, which can be formed, for example, simply by a bolt with an eccentric disc arranged thereon and subsequently referred to as an eccentric for the sake of simplicity, the sickle can first be introduced into an area where there is still a relatively large clearance between Sickle and inner gear and outer internal gear consists, after which it can then be pushed into the tapered gap by means of the adjustment mechanism, whereby a sufficiently small game between sickle's rule and gears is adjustable. The adjusting mechanism, for example in the form of the eccentric described above, can be set after the necessary play has been set, which can be done, for example, by means of a locking screw, gluing or welding. The pump can then be further assembled. Description of the figures

The following are possible embodiments of the invention

Pressure supply device explained in more detail with reference to drawings.

Show it :

Fig. 1: a first possible embodiment of a gear pump of a pressure supply device according to the invention, wherein the gear pump is designed as a 1-stage gear pump, and the drive shaft is inter alia via the inner gear of the gear pump Gela Gert;

FIG. La: a section through the internal gear pump according to FIG. 1;

FIG. 1b: a section through the area of the gear pump according to FIG. 1, in which the fixed outer parts of the gear pump are welded together;

Fig. Lc: a slightly modified embodiment of the gear pump ge compared to the embodiment shown in Figure la with Schllitz ter sickle and its mounting via a bolt;

Fig. Id: Cross-sectional view through a gear pump with internal

Gear wheel, sickle and outer inner tooth ring, the sickle being displaceable by eccentric and lockable or fixable in different positions;

FIG. 1e: enlarged detail from FIG. 1d;

Fig. 2: an embodiment of the gear pump with a ball bearing between the inner ring gear and the outer ring, the drive shaft in the gear pump is also superimposed on the inner gear GE;

3: an embodiment in which the drive shaft is mounted in the gear pump by means of roller bearings; Fig. 4: a 2-stage gear pump with partial storage of the drive shaft to in the gear pump;

Fig. 5: a 2-stage gear pump, the drive shaft being supported completely, i.e. exclusively in the gear pump;

Fig. 6: an engine mounting both in the drive housing and in the

Gear pump, wherein the first bearing is formed with magnetic Verspan voltage and the second bearing is arranged in the gear pump;

6a: an engine mounting with both bearings in the gear pump;

7: a brush motor with a 1-stage gear pump;

7a: a brush motor without a gear pump;

Fig. 8: a mounting device for a gear pump according to the invention pe.

Figures 1 and la show a possible embodiment of an internal gear pump with drive shaft 1, internal gear 2, internal ring gear 3, guide part in the form of a sickle 5, the latter being connected via the bolt 6 to the outer disks 7.1 and 7.2 and thus fixed. The aforementioned parts are embedded in the two outer disks 7.1 and 7.2 together with the outer ring 4, the outer ring 4 being connected to the two outer disks 7.1 and 7.2 by welding LS, which is shown enlarged in FIG. The two outer disks 7.1 and 7.2 together with the outer ring 4 form the pump housing ZG of the gear pump Z, which is mounted in the recess 18b of the wall 18. The wall 18 forms a flange on or with which the drive housing can be fastened to the hydraulic housing.

In Fig. Lb it is shown that the outer diameter of the areas 7.1a, 7.2a and 4a of the outer disks 7.1, 7.2 and the outer ring 4 provided for the welding LS is smaller than the largest outer diameter D _{A of} the parts, so that the assembly in the recess 18b, which can be formed by means of a hole, is not hindered by the weld LS. The Monta ge and adjustment of these parts is described in FIG.

The gap or play between the rotating inner gear 2 and the inner ring gear 3 to the gear pump housing ZG, which is formed by the outer disks 7.1 and 7.2 and above all by the outer ring 4, is decisive for the losses due to leakage flow. The disks 7.1, 7.2 and the outer ring 4 can be manufactured very precisely by flat grinding, so that small gaps or clearances are possible.

The inner gear 2 is guided on the drive shaft 1 through the short collar 11. This has the advantage that small angular tolerances between gear 2 and shaft 1 do not lead to gear 2 jamming in the housing ZG. The torque to gear 2 is transmitted via a driver 10. This torque is also transmitted by the locking bolt 9 to the wall application or the flange 18 transferred. At the front, both suction and pressure connections act with seals, which are connected to the hydraulic housing HCU.

The outer disk 7.2 is provided with a seal 14 to the hydraulic housing HCU. The shaft seals 13.1 and 13.2 also act. The drive shaft 1 also has a shaft journal 8, which is required for mounting the pump housing ZG, see FIG. 8. To reduce the friction due to the pressure forces on the inner ring gear 3, a roller bearing, needle or ball bearing 17a, see FIG. 2, can be installed between the latter and the outer ring 4.

Fig. La shows the gear pump Z in section. The so-called sickle 5, which is made in one piece with a central bearing 6, plays an important role in the sealing function. Here act on the sickle 5, the pressure forces of the enclosed areas. The sickle 5 is here centrally mounted on a pin 6, as is known from the prior art. The connections for suction S and the pressure outlet with pressure P with direction of rotation are also shown in FIG. Of course, the currents will change direction as soon as the gear 2 rotates in the other direction, whereby the suction side S becomes the pressure output P and vice versa.

As shown in Figure lc, it is also possible to design the sickle 5 th in two parts by a two-sided fixation 6a, 6b without a shaft with a compensating spring, which results in an even better sealing function. Here, the pressure equalization can be optimized through recesses on the sickle 5 and also axially to the outer disks 7.1 and 7.2.

Instead of the internal gear pump, a gerotor pump can also be used, which does not have a sickle and a fixed internal gear rim. The inner gear is mounted eccentrically on an eccentric being driven by the drive shaft and rolls in the stationary internal gear rim. A trochoidal tooth system is preferred as the tooth system. The leakage oil must be diverted to S via the leakage flow channel in order to relieve the seals.

Figures ld and le show a further possible embodiment of a gear pump with an inner gear 2 and an outer inner toothed ring 3 as well as a sickle 5, which lies in a gap 52 formed by the inner gear 2 and the outer inner toothed ring 3, the gap 52 in Tapered clockwise. The sickle 5 has a first circular arc-shaped bearing surface 54, with which it rests on the radially outer end faces 2b of the teeth 2a of the inner gear 2. The sickle 5 has a further second circular arc-shaped contact surface 55, with which it rests on the radially inwardly facing end faces 3b of the teeth 3a of the outer inner tooth ring 3. So that a sufficiently small play between the sickle 5 and the teeth 2a, 3a can be set, the sickle has a particularly elongated recess 51 through which an eccentric bolt 5c extends, the cam of the eccentric 5c with the inner wall 50 of the elongated hole 51 together men acts or is applied to this area by area. The eccentric 5c itself is, for example, in or on at least one or both outer disks 7.1, 7.2 rotatably Gela Gert and can be locked, fixed or attached to at least one outer disk 7.1, 7.2 by a locking mechanism, not shown in Figures ld and le, so that after setting the necessary Game the sickle 5 can no longer move relative to the inner gear 2 and the outer ring gear 3 during operation of the pump and the game is permanently maintained.

The radii of the circular arc-shaped contact surfaces 54 and 55 are matched to those of the tip circles of the inner gear 2 and the outer inner toothed ring 3, so that as many teeth as possible fit sufficiently sealingly 2a, 3a to the contact surfaces 54, 55.

For pressure equalization between the contact surfaces 54 and 55, at least one channel 5k, which is designed, for example, as a radial bore 5kb or channel or groove 5kr, can be provided so that a pressure-equalizing exchange of the conveying medium between the contact surfaces 54 and 55 or the chambers Rpi or Rp ₂ can take place.

FIG. 1e shows an enlarged detail from FIG. 1d in the area of sickle 5.

FIG. 2 shows the same construction of the gear pump Z according to FIG. 1, with the difference being a sliding bearing 16 on both sides of the drive shaft 1 in the two outer disks 7.1 and 7.2. This eliminates the need for a separate engine mount, as shown in Figures 6 and 6a. The leakage oil channels 15 are modified here.

FIG. 3 also shows the similar structure of the pressure supply device according to FIGS. 1 and 2, with the difference in the use of roller bearings 17 to minimize bearing friction. In addition, the outer disk 7.1 and the outer ring 4 are replaced by the part 7.1b, which is pot-shaped and accommodates the inner gear 2 and the inner ring gear 3. In this design, only one weld LS is required, which connects the part 7.1b and the outer pane 7.2 materially.

Fig. 4 shows a 2-stage internal gear pump. This pump uses the same elements, such as drive shaft 1, inner gear 2, inner ring gear 3, guide part (sickle) 5, fixings 6 and 6a., Driver 10, outer ring 4, all of which are provided twice. The additional difference lies in the suction channel S and in the overall length and the central disk 19, which also contains a channel from the P output of the 1st stage to the suction channel of the 2nd stage.

Here, too, an additional motor mounting in the drive housing is necessary compared to the pressure supply device according to FIG. 5, which in principle corresponds to the mounting of FIG. 2 and does not require any additional motor mounting.

Fig. 6 shows a representation of the entire structural unit consisting of motor 22, pump Z, HCU and ECU, which is able to exercise the pressure regulation and control for systems such as brakes, gears, etc. The main focus here is on the combination of motor and pump. The pump is arranged in the bearing flange 18, as shown in FIGS. 1 to 5, or is attached to the HCU or ECU in a separate pump housing 40, as shown in the upper half of the figure. In Fig. 6 the simplest version according to Fig. 1 is shown, which requires an additional motor bearing 20 in which the shaft 1 is mounted. As usual, the motor is composed of rotor 21, which is connected to shaft 1 via driver 10a. The rotor 21 is axially preloaded by its force via a permanent magnet 30a in the housing 30. This is a solution for the motor manufacturer who manufactures and tests the motor with housing 22 and stator and winding 23 and delivers it to the system supplier. Here the motor is tested without a pump with an auxiliary shaft. Thereafter, when the shaft is removed, the rotor is centered by the axial magnetic force, so that the shaft 1 can then be assembled with the rotor during final assembly. The permanent magnet 30a can, with its force acting axially on the rotor 21, if it is large enough, compensate for tilting forces of the rotor, so that no further mounting of the rotor 21 in addition to the bearing 20 is necessary. A sufficiently large clearance can or should be provided in the gear pump.

The drive housing must also be joined and fastened here with the flange 18 at 25a - shown in the lower half of the figure, e.g. B. with springs, which are attached in segments over three connections the. A housing seal 31 is also necessary here. It can be fastened by caulking, at 25 from the engine flange with HCU or ECU, see upper half of the figure 28. The pump version with pump housing is shown here. The motor is shown here as a brushless motor that needs a Mo torsensor for commutation and control of the volume delivery of the pump. This motor sensor is arranged at a distance from the drive housing 22, with a sensor shaft 26 which is net or attached to the drive shaft 1 and carries a sensor target 27. This target 27 acts on the sensor element 28, which is arranged on the circuit board of the ECU.

The winding is connected to the ECU via contact bars 24.

The motor with bearing flange 18 can be connected directly to the hydraulic housing HCU, which valves or other hydr. Includes components to be connected to the pump. If this is not the case, a connection of the drive housing 22, 18 directly to the housing of the ECU is possible.

It is also possible to assign the gear pump Z in a pump housing 40 which is connected directly to the hydraulic housing HCU, as shown in FIG. 6 in the upper half of the drive shaft 1. Before the pump housing 40 and hydraulic housing HCU or pump housing 40 and ECU are assembled, the gear pump Z is first integrated or mounted in the pump housing 40, the rotor 21 then being pressed onto the shaft 1 and then assembled with the bearing 20. Here, the tensile force of the magnet 30 can also act on the rotor 21 and the bearing 20, so that the bearing acts like a four-point bearing. The motor housing 22 is thus connected to the gear pump Z and its pump housing 40 and, in the next step, can be connected to the hydraulic housing HCU or the electronics housing ECU. For this purpose, the fastening screw 41 is used. The shaft 1 is previously centered in the outer disks 7.1 and 7.2 so that the pump housing 40 is centered with the shaft 1 before the screw connection to the hydraulic housing HCU or the electronics housing ECU.

The pressure supply device according to Fig. 6a uses a 2-stage pump with long sliding or roller bearings according to Fig. 2, 3 and 5, wel- does not require separate motor storage. The motor structure with the housing is accordingly simplified. The rotor 21 sits with driver 10a on the motor shaft and is axially connected to the locking ring. The pump housing protrudes slightly into the HCU here.

Fig. 7 shows a 1-stage gear pump with a brush direct current motor, which is taken from DE 102013217257. Instead of the so-called piston return pump for ABS, the gear pump according to the invention is now used. This can correspond to the embodiments according to FIGS. 1, 2 and 3. 1 is shown with drive shaft 1, inner gear 2, inner ring gear 3 and the welded disks 7.1, 7.2 with outer ring 4. Corresponding to a pump version as shown in FIGS. 2, 3 and 6a, a motor bearing can also be dispensed with.

Fig. 7a shows the delivery condition from the engine manufacturer without gear pump, only with drive shaft 1. For the final test, the shaft 1 is mounted in the bearing flange 18.

8 shows the assembly device for welding the disks 7.1 and 7.2 together with the outer ring 4. For this purpose, a sleeve 37 is pushed over the drive shaft and axially fixed with the locking ring. The disks 7.1, 7.2 and the outer ring are then centered via the centering sleeve 35. On the opposite side, the washers 7.1, 7.2 are axially clamped together with the outer ring with the nut 34 via the mounting disk 33. After removal of the centering sleeve, LS can then preferably be laser welded. For this purpose, the sleeve is clamped in a rotatable manner. As Fig. Lb shows, the diameter of the weld is smaller, so that the later assembly in the flange is not hindered. Reference list

1 drive shaft

lb end of the drive shaft

2 internal gear (toothed ring)

3 internal ring gear

4 outer ring

5 guide part (sickle)

5a 2-part sickle

5b balance spring

5c eccentric

5k channel

5kr channel or groove

5kb drilling

6 Fixation of the sickle

6a fixation alternative

7.1 Outer pane 1

7.2 Outer pane 2

8 threaded studs

9 Anti-twist device

10 carriers

10a driver to the rotor

11 guide band

12 waves

13.1 Seal

13.2 Seal

14 Outer pane seal

15 leakage flow channel

16 plain bearings

17 rolling bearings

17a rolling bearings

18 wall of the drive housing, which is the first housing part of the

Motor housing, in particular as a bearing flange or side wall, is formed

18b recess in the side wall

18f window-like recess for drive shaft

18k channel

19 center disk

20 engine mounts

21 rotor

21a stator

22 motor housing 23 Motor winding

24 Motor contact

25 Housing mounting

25a alternative housing attachment

26 sensor shaft

27 target

28 Sensor element on circuit board

29 Circlip

30 housing with magnet 30a

30a magnet

31 Housing seal

32 brush DC motor

33 mounting washer

34 mother

35 centering sleeve

36 moment support

37 sleeve

38 Circlip

39 Rolling Bearings

40 pump housing

41 fixing screw

45 Side wall of the hydraulic housing

46 recess in the side wall 46 of the hydraulic housing

48 channel for electrical cables

50 eccentric contact surfaces

51 elongated hole

52 gap

53 Direction of tapering of gap 52

54 first circular arc-shaped contact surface

55 second circular arc-shaped contact surface

B Axial width of the inner gear 2

D seal

S Suction connection with seal

P pressure connection with seal

LS laser welding

HCU hydraulic block

HCUsi side of the hydraulic housing facing the drive housing

HCU _S 2 side of the hydraulic housing facing the electronics housing

ECU electronic control unit

Sa, Pa orifices of channels S and P

Z gear pump

ZG gear pump housing

Claims

1. Pressure supply device with an electric motor drive (21, 23) arranged in a drive housing (18, 22) and a gear pump (Z) driven by the sem, the drive (21, 23) having a stator (23) and a rotor (21 ) and the gear pump (Z) has a gear (2) coupled to the rotor (21), a wall (18, 40) being arranged between the rotor (21) and the gear (2), characterized in that that at least one seal (13.1) is arranged between the rotor (21) and the gearwheel (2) in such a way that the Ro tor (21) is a dry-running rotor that is not surrounded by and / or surrounded by the medium conveyed by the gearwheel (2) is.

2. Pressure supply device according to claim 1, characterized in that the drive housing (18, 22) has a side wall (18) on which the gear pump (Z) is arranged or in which, in particular in a recess (18b) of the side wall (18) , the gear pump (Z) is at least partially or completely inserted.

3. Pressure supply device according to claim 1 or 2, characterized in that the wall (18, 40), in particular in the form of a Be tenwandung of the drive housing or a pump housing (40), of a with the rotor (21) rotatably connected to the drive shaft (1 ) is gripped, the gear wheel (2) non-rotatably connected to the drive shaft (1) or coupled to the drive shaft (1) via an interposed gear and / or a coupling.

4. Pressure supply device according to one of claims 1 to 3, characterized in that the drive (21, 23) rests on a hydraulic housing (HCU) with at least one valve and / or hydraulic lines or channels arranged therein or forms a unit with it , the gear pump (Z) both in the recess (18b) of the side ten wall (18) as well as in a recess (45) of the hydraulic housing (HCU), the openings of the recesses (18b, 41) facing one another.

5. Pressure supply device according to one of the preceding Ansprü surface, characterized in that the recess (18b) is open towards the hydraulic housing (HCU), in particular is cup-shaped.

6. Pressure supply device according to one of the preceding claims, characterized in that at least one seal (D) in the side wall (18) and / or in a first hydraulic housing side wall (40) corresponding to the side wall (18) is angeord net and / or the at least one seal (14), in particular in the cylindrical outer wall, of at least one bearing plate (7.1, 7.2) is arranged.

7. Pressure supply device according to one of the preceding Ansprü surface, characterized in that the drive housing (18, 22) is formed at least in two parts, wherein the side wall (18a) is part of a first housing part (18).

8. Pressure supply device according to claim 7, characterized in that a second housing part (22) is cup-shaped and accommodates the Sta tor (23) and the rotor (21) of the electric motor drive.

9. Pressure supply device according to one of the preceding Ansprü surface, characterized in that the gear pump (Z) is arranged in a pump housing (40) which is attached to the drive housing (18, 22), a hydraulic housing (HCU) or an electronics housing (ECU) is attached.

10. Pressure supply device according to one of the preceding Ansprü surface, characterized in that the rotor (21) is coupled to the gear (2) by means of a drive shaft (1) directly or via a transmission.

11. Pressure supply device according to one of the preceding claims, characterized in that the gearwheel (2) is non-rotatably connected to the drive shaft (1) by means of a non-positive connection or by means of a form fit, which is formed in particular by means of a pin or serration .

12. Pressure supply device according to one of the preceding Ansprü surface, characterized in that the gear pump (Z) either

- An internal gear pump with, in particular movable or

fixed, single or multi-part, especially two-part, sickle (5),

- an external gear pump or

- a gerotor pump

is.

13. Pressure supply device according to the preamble of claim 1 or according to one of the preceding claims, characterized in that the internal gear pump (Z) in addition to the gear (2), which is designed as an inner gear, also an outer internal gear (3) and a sickle ( 5), the rotor (21) being coupled to the inner gear (2) by means of a drive shaft (1) directly, via a coupling and / or via a gear.

14. Pressure supply device according to claim 13, characterized in that the sickle (5) is displaceably mounted in the gear pump (Z), in particular between two bearing parts or fixings (6, 6a).

15. Pressure supply device according to claim 13 or 14, characterized ge

indicates that the sickle (5) is designed in one or two parts (5a, 5b).

16. Pressure supply device according to one of claims 13 to 15,

characterized in that the sickle (5) by means of an adjustment mechanism (6, 6a), in particular in the form of a spring or a twistable part (5b), in particular in the form of an eccentric (5c), which is designed as a pin, relative to Internal gear (2) adjustable and / or is lockable.

17. Pressure supply device according to one of claims 13 to 16,

characterized in that the sickle (5), in particular its contact surface with the inner gear (2), and / or the teeth of the inner gear (2) at their outer radial ends, depressions, in particular in the form of grooves, which are in particular extend in the circumferential direction, have to equalize the pressure.

18. Pressure supply device according to one of claims 13 to 17,

characterized in that the sickle (5) has eccentric contact surfaces (50), which are formed in particular by the inner walls of an elongated hole (51), which interact with an eccentric (5c) and, by rotating the eccentric (5c), the sickle (5) displaceable in the plane of the inner gear (2), in particular the play between the inner gear (2) and the outer inner ring gear (3) is adjustable and can be held in position.

19. Pressure supply device according to claim 18, characterized in that the sickle (5) can be moved by rotating the eccentric (5c) in the gap (52) located between the inner gear (2) and the outer ring gear (3), in particular in Direction of the taper (53) of the gap (52) can be pressed.

20. Pressure supply device according to one of claims 13 to 19,

characterized in that the sickle (5) has a first circular arc-shaped contact surface (54) for contact with the end faces (2b) of the teeth (2a) of the inner gear (2) and a further second arc-shaped contact surface (55) for contact with the end faces (3b) of the teeth (3a) of the outer internal gear rim (3).

21. Pressure supply device according to claim 20, characterized in that the radius of the first circular arc-shaped contact surface (54) is adapted to the tip circle or outer radius of the inner gear (2) or these are the same size, and that the radius of the second circular gene-shaped contact surface (55) on the tip circle or inner radius of the outer inner ring gear (3) is adapted or these are the same size.

22. Pressure supply device according to one of claims 13 to 21,

characterized in that a locking mechanism for the eccentric (5c) is provided, with which the eccentric (5c) can be rotated and / or locked, in particular from the outside through the pump housing.

23. Pressure supply device according to one of claims 13 to 22,

characterized in that the eccentric (5c) is mounted and / or non-rotatably mounted in or on at least one outer disk (7.1, 7.2), in particular can be fastened or fixed by means of a locking screw, welding or gluing.

24. Pressure supply device according to one of claims 13 to 23,

characterized in that the sickle (5) has at least one, in particular radially extending, channel (5k), in particular for pressure compensation, which is formed in particular by a channel or groove (5kr) or a bore (5kb), and which connects the two contact surfaces (54, 55) to one another.

25. Pressure supply device according to one of the preceding claims, characterized in that the drive shaft (1) is either a) in the drive housing (22) on the one hand, and in the gear pump (Z) and / or in the hydraulic housing (HCU) on the other hand, or b) only in the gear pump (Z) or c) in the hydraulic housing (HCU) and in the drive housing (22) or d) in the gear pump (Z) and in the hydraulic housing (HCU) or is supported by means of suitable bearings, in particular radial bearings.

26. Pressure supply device according to one of the preceding claims, characterized in that the drive shaft (1) is non-rotatably connected to the rotor (21).

27. Pressure supply device according to one of the preceding claims, characterized in that the side wall (18) has a window-like opening (18f), in particular in the form of a bore, through which the drive shaft (1) extends, one being the drive shaft (1) comprehensive ring seal (13.1) serves to seal the window-like opening (18f).

28. Pressure supply device according to one of the preceding claims, characterized in that the pump housing (40) has a window-like opening, in particular in the form of a bore, through which the drive shaft (1) extends, one of which is the drive shaft (1 ) Comprehensive ring seal (13.1) is used to seal the window-like opening.

29. Pressure supply device according to one of the preceding claims, characterized in that the side wall (18) or the first housing part (18) is designed as a bearing flange and fastened or fastened to the hydraulic housing (HCU) by means of fastening means, in particular screws is.

30. Pressure supply device according to one of the preceding claims, characterized in that on the first hydraulic housing side (HCUsi) opposite side (HCU _S2 ) of the hydraulic housing (HCU) a control and regulating device (ECU) is arranged with its housing (ECU _G ) .

31. Pressure supply device according to claim 30, characterized in that the drive shaft (1) or a sensor shaft (26) arranged thereon extends into the hydraulic housing (HCU), in particular as far as its opposite side (HCU _S2 ), or the hydraulic housing (HCU) takes full action.

32. Pressure supply device according to claim 31, characterized in that the drive shaft (1) or the sensor shaft (26) arranged thereon at its one end (26a) which is the end of the area of the drive shaft (1) or the sensor shaft (26 ) forms, which in the hydraulic likhousing (HCU) extends in or through this completely, in particular into the housing (ECU _G ) of the control unit (ECU) he stretches, a target (27) carries.

33. Pressure supply device according to one of the preceding claims, characterized in that the gear pump (Z) has a first bearing plate (7.1) and a second bearing plate (7.2), which are formed in particular by disks, between which the gears (2, 3) and the outer ring (4) are arranged.

34. Pressure supply device according to claim 33, characterized in that the outer ring (4) is connected to both the first bearing plate (7.1) and the second bearing plate (7.2), in particular welded, preferably welded all round, and is a structural unit .

35. Pressure supply device according to one of claims 1 to 32,

characterized in that the gear pump (Z) has a cup-shaped part (7.1b) and a bearing plate (7.2), which is formed in particular by a disk, the gears (2, 3) in the cup-shaped part (7.1b) lie in and the cup-shaped part (7.1b) and the La gerplatte (7.2) are connected to one another, in particular cohesively by welding, soldering or gluing.

36. Pressure supply device according to one of the preceding claims, characterized in that the gear pump (Z) rotates firmly in the by means of an anti-twist device (9), in particular having a bolt which engages in a further recess (18c) of the recess (18b) Recess (18b) of the side wall (18) rests.

37. Pressure supply device according to one of the preceding claims, characterized in that in the first hydraulic housing side wall (46) corresponding to the side wall (18) or the pump housing (40), orifice openings (Sa, Pa) for at least two channels (S, P) are provided, with one channel (S) for the suction connection and one channel (P) for the pressure connection of the gear pump (Z) serves.

38. Pressure supply device according to claim 36, characterized in that a seal (D) rests in the mouth opening (Sa, Pa) and / or a seal (D) rests in a groove (47) in the hydraulic side wall (46) and the mouth opening ( Sa, Pa), which also rests in a sealing manner on the second bearing plate (7.2).

39. Pressure supply device according to one of the preceding claims, characterized in that the internal gear (2) has a maximum axial width (B), the axial length of the contact surface with which the internal gear (2) rests on the drive shaft (1), is shorter than the maximum axial width (B) and / or the internal gear (2) is arranged tiltably on the drive shaft (1).

40. Pressure supply device according to one of the preceding claims, characterized in that the electrical connections (24) of the electrical drive (21, 23) through a channel (18k) of the side wall (18) and a channel (48) of the hydraulic housing (HCU ) are passed through.

41. Pressure supply device according to one of the preceding claims, characterized in that the drive shaft (1) is mounted with its second end (Ib) in the second housing (22).

42. Pressure supply device according to one of the preceding claims, characterized in that the gear pump (Z) is arranged wholly or partly next to the rotor (21) in the axial direction.

43. Pressure supply device according to one of the preceding claims, characterized in that the drive shaft (1) is rotatably supported in the pot-shaped part (7.1b) and / or a bearing plate (7.1, 7.2), in particular by means of roller bearings (17).

44. Pressure supply device according to one of the preceding claims, characterized in that a magnet (30a) for forming a magnetic preload (F) of the motor bearing and / or exercising a axial force (F) is provided on the rotor (21) which is arranged on the housing of the motor.

45. Pressure supply device according to one of the preceding claims, characterized in that the pressure supply device serves as a pressure source for a brake system and / or a transmission.

46. Pressure supply device according to one of the preceding claims, characterized in that several electric motors and gear pumps (Z) are arranged in a drive housing and / or several gear pumps are arranged in or on a hydraulic housing (HCU).

47. Pressure supply device according to one of the preceding claims, characterized in that several pressure supply devices are combined to form a module or structural unit.

48. Pressure supply device according to one of the preceding claims, characterized in that a bearing, in particular in the form of a ball or roller bearing, between the radial outer wall of the inner ring gear (3) and the outer ring (4) or surrounding the inner ring gear (3) The cylindrical inner wall of the cup-shaped part (40) are provided in order to keep the friction as small as possible.

49. Brake system or transmission with a pressure supply device according to one of the preceding claims.