CN111133193A

CN111133193A - Pump housing of a hydraulic unit having a pump receptacle

Info

Publication number: CN111133193A
Application number: CN201880061785.XA
Authority: CN
Inventors: T·赞德尔; M·勒夫勒
Original assignee: Robert Bosch GmbH
Current assignee: Robert Bosch GmbH
Priority date: 2017-09-25
Filing date: 2018-07-30
Publication date: 2020-05-08
Also published as: WO2019057373A1; DE102017216903A1

Abstract

The invention relates to a pump housing (56) of a hydraulic assembly (10) of a vehicle brake system, comprising a first housing section (58) and a second housing section (62) and at least one pump receptacle (26) for receiving a pump element. The at least one pump receptacle (26) is arranged in the first housing section (58) and the first housing section (58) has a first housing thickness (60) and the second housing section (62) has a second housing thickness (64), wherein the second housing thickness (64) is smaller than the first housing thickness (60).

Description

Pump housing of a hydraulic unit having a pump receptacle

Technical Field

The invention relates to a pump housing of a hydraulic unit of a vehicle brake system, comprising a first housing section and a second housing section and at least one pump receptacle for receiving a pump element. The invention further relates to the use of such a pump housing in a hydraulic unit of a vehicle brake system. A similar pump housing is known, for example, from DE 102008055000 a 1.

Background

Vehicle brake systems of the type mentioned are used to slow down motor vehicles, in particular passenger cars or trucks. For this purpose, a hydraulic unit is installed in the vehicle brake system, in which a plurality of pump elements are used to supply brake fluid. In this way, together with further functional elements, a regulated brake pressure can be provided in the associated brake circuit. The regulated brake pressure is necessary above all for the function of an anti-lock braking system (ABS), an anti-slip control system (ASR) and an Electronic Stability Program (ESP).

The individual pump elements are arranged in a pump receptacle in a pump housing, which is usually provided in the form of a block with a square hydraulic block. At least one bore hole serving as a pump receptacle is provided therein, which bore hole is arranged perpendicularly into the bore hole for the shaft receptacle. A drive shaft for driving the pump element by means of an eccentric is accommodated in the shaft receptacle. For this purpose, the drive shaft is coupled in a force-transmitting manner to a drive motor in the motor housing, which drive motor is arranged on the outer side of the hydraulic block. In addition, additional bores for different hydraulic components and lines connected to one another are provided in the hydraulic block. The pump housing thus forms the core region of the hydraulic assembly.

Disclosure of Invention

According to the invention, a pump housing of a hydraulic unit of a vehicle brake system is provided, which has a first housing section and a second housing section and at least one pump receptacle for receiving a pump element. At least one pump receptacle is arranged in the first housing section. Furthermore, the first shell section has a first shell thickness and a second shell thickness, wherein the second shell thickness is smaller than the first shell thickness.

The pump housing is therefore essentially divided into two housing sections, wherein the first housing section comprises at least one pump receptacle. According to the invention, this section has a shell thickness, which is greater than the second shell thickness of the second shell section, with its first shell thickness. The pump housing therefore has a thickening in the section in which the at least one pump receptacle is arranged compared with at least a second housing section of the remaining pump housing.

The respective housing thickness may be, in particular, the maximum housing thickness, which is preferably of identical or uniform design over the entire associated housing section.

In contrast, the second housing section has a smaller housing thickness than the first housing section with its second housing thickness, wherein the first housing section has its first housing thickness. The pump housing according to the invention is therefore particularly small overall in terms of its volume. Less material, weight and installation space are required on the second housing section than on the first housing section. This saving in material is particularly great for pump housings which are preferably designed as hydraulic blocks, particularly preferably made of extruded profiles in the form of rods. So configured, the pump housing is filled with material and a lot of material can be saved by means of the smaller second housing thickness. Material costs and weight can be significantly reduced. The pump housing according to the invention can thus be constructed smaller and lighter than conventional pump housings which generally have a housing thickness which remains the same.

At the same time, the pump housing according to the invention is surprisingly nevertheless sufficiently stable for reliably withstanding the loads occurring in and on the pump housing during operation. It has already been shown that it is sufficient to provide the first housing section, which comprises the at least one pump receptacle, with its respectively necessary first housing thickness. In addition to the individual pump receptacles, the solenoid valves and the transverse bores associated therewith first determine the housing thickness. Furthermore, a pump element, which comprises a pump piston supported on an eccentric bearing, is to be accommodated in the pump accommodation in the first housing section. During the rotational movement of the eccentric bearing, the pump piston moves back and forth along its piston axis. As a result, a translatory pump movement occurs in the first housing section during operation. In addition, oscillations or vibrations extending transversely to the piston axis increase the load on the pump housing, which oscillations or vibrations are transmitted during rotation substantially by the eccentric bearing to the pump piston supported there. As a result, the pump housing is subjected to relatively high loads in its first housing section. This main load region can be sufficiently stabilized only by a first housing thickness or thickening in the pump region which is greater than the second housing thickness.

In the second housing section with the smaller second housing thickness, the additional required functional elements and lines can be accommodated at the same time, for which the second housing thickness is sufficient. Preferably, known interfaces and hydraulic assemblies can be used for this purpose without changes. The production of the pump housing according to the invention and the installation thereof in the known hydraulic unit can be carried out particularly easily.

Preferably, the first housing section is provided at least approximately with a first square shape and the second housing section is provided at least approximately with a second square shape. In this case, the first square shape has a first edge length in one spatial direction and the second square shape has a second edge length in the same spatial direction, wherein the second edge length is smaller than the first edge length. Preferably, the second edge length is used to define the second shell thickness, and the first edge length is used to define the first shell thickness. Such a pump housing can be produced from extruded materials easily in terms of production technology.

According to the invention, a third housing section is advantageously provided, which is arranged opposite the second housing section with respect to the first housing section. In this case, the third housing section has a third housing thickness and the third housing thickness is likewise configured to be smaller than the first housing thickness. With the smaller third housing thickness, the weight of the pump housing can be further reduced in addition to the smaller second housing thickness. At the same time, the first housing section is arranged between the second and third housing sections. With such an arrangement, the forces can be distributed particularly uniformly from the main load region of the first housing section to the second and third housing sections.

Furthermore, according to the invention, the pump housing advantageously has an outer surface which is provided with a transition, in particular with a step, from the first housing section to the second housing section and/or to the third housing section. The transition can be shaped differently and can be adapted in its shape in a targeted manner to further components in the associated hydraulic assembly. This shape is particularly easy to achieve in terms of manufacturing technology for block-shaped pump housings during the extrusion process from the extruded profile in the extrusion direction by means of a correspondingly shaped die. The shape of the transition in its cross section is preferably designed in particular obliquely and/or convexly, in particular in a concave configuration with respect to the pump housing. Such an inclined or arched transition prevents dirt from being deposited there. The transition is particularly preferably designed as a step in a particularly material-saving manner.

Furthermore, according to the invention, the outer surface provided with the transition advantageously represents the contact side of the pump housing for mounting the motor housing. In this case, the contact side includes not only the first contact side of the first housing section but also the second contact side of the second housing section and/or the third contact side of the third housing section. Preferably, the motor housing is arranged on the first, second and third contact side with a particularly uniform force transmission. The unevenness of the outer surface provided with the transition can be compensated for by means of a motor housing which is formed complementarily to the contact flank. A correspondingly complementarily formed connecting flange or motor flange is also possible, which connects the motor housing to the contact side of the pump housing. This need for unevenness to be compensated for is compensated for by a decisive advantage. The advantage is that a free space filled with air is formed relative to the motor housing to be mounted by means of the transition between the first housing section and the second and/or third section. The free space can be used as a leakage chamber for receiving the leaked hydraulic fluid, without additional installation space in the vehicle brake system having to be consumed.

According to the invention, it is furthermore advantageous if the first housing section is provided with a recess on the contact side of the pump housing, in which recess the motor housing is intended to be arranged in part. By means of the recess, the motor housing can be easily mounted on the contact side, that is to say on the outer side of the pump housing on which the transition is provided. No special configuration of the motor housing and/or its motor flange, which is complementary to the contact flank on the first housing section, is required. The known shapes of the motor housing and motor flange can be applied. For this purpose, the motor housing is provided with a longitudinal wall along the motor axis and with a transverse wall extending transversely to the longitudinal wall. Preferably, the transverse wall is arranged so as to be circumferentially surrounded by the longitudinal wall and so as to be displaced in the interior of the longitudinal wall into the interior of the motor housing. The excess of the longitudinal wall of the motor housing formed thereby can be arranged partially in the recess of the first housing section. In the case of an excess or no excess, the motor flange is preferably arranged on the motor housing adjacent to the longitudinal wall, which should be arranged in the recess. It is particularly preferred that the motor housing is to be arranged in the recess in a stable manner, in particular on its motor flange. Furthermore, the recess is used to provide a marking for the correct position and dimensional accuracy of the mounting of the motor housing on the pump housing. Furthermore, it has been shown that the recess does not adversely affect the stability of the first housing section. Furthermore, the recess has no influence on the first housing thickness according to the invention, in particular the maximum housing thickness of the first housing section.

Furthermore, according to the invention, it is preferred that the recess of the first housing section is provided with a first base surface, that the second housing section is provided with a second base surface on the contact-side surface of the pump housing, and/or that the third housing section is provided with a third base surface on the contact-side surface of the pump housing. In this case, a flat contact surface for mounting the motor housing is formed together with the first and second and/or third bottom surfaces. On the flat contact surface formed in this way, the motor housing can be mounted without a shaping of the motor housing which is to be matched complementarily to the transition. More precisely, the transition on the outer surface can be compensated by the recess with its first base surface in such a way that a flat contact surface is formed with the second and/or third base surface. In addition, in this contact surface, the forces which are emitted from the motor housing during operation in the installed state act on the contact surface in a particularly uniform and widely distributed manner over the entire plane of the contact surface. The flat contact surface can thus also form a particularly stable sealing surface for the motor housing. Furthermore, the previously known motor housings can be arranged on such a flat contact surface without significant modifications in the housing geometry.

In addition, according to the invention, the recess advantageously has the shape of a part of a ring in its cross section and the ring is arranged in particular concentrically to the motor axis of the motor housing to be mounted. The circle represents the area between two concentric rings. In this case, a part of the ring is in particular a ring segment, which is formed by two partial segments of the same ring. Such a part of the annular ring can preferably be produced easily in terms of production technology by means of a milling tool which is circular in cross section by milling out the first housing section on the contact surface. Furthermore, the recess is matched with the known motor housing with its outer contour and/or with its motor flange with its circular cross section. In particular, for this purpose, a part of the ring is arranged concentrically to the motor axis. In this way, the drive shaft of the motor can be held concentrically by the motor housing in the shaft receptacle in the arrangement first housing section for the motor housing mounted there. With such a holding, the forces occurring during rotation of the drive shaft can be distributed particularly uniformly.

Furthermore, according to the invention, a part of the ring is advantageously provided with an outer circumference and an inner circumference, wherein the motor housing is arranged in the recess with almost no spacing on the outer circumference and at a spacing from the inner circumference. The outer circumference is defined by an outer radius and the inner circumference is defined by an inner radius that is smaller than the outer radius. In this case, the motor housing is preferably supported radially on the outside by force on the recess, almost without play. An additional first bottom surface of the recess is formed radially inwardly at a distance from the inner circumference. The first housing thickness of the first housing section is thereby reduced over a large extent in its recess. This additional material reduction serves as a further weight saving.

As an alternative to the portion of the circular ring, the recess has another shape in its cross section. A simple shape similar to a square or polygonal portion having an outer periphery and a concentric inner periphery, respectively, is preferred.

With such a cross section, sufficient space for the required hydraulic components and sufficient material for the stable punching of the required motor bearings there are still left radially inside the first housing section. Radially on the outside, a material web remains on the first housing section, with which material web sufficient material is present for the pump element to be able to be punched into the pump receptacle.

Furthermore, according to the invention, a shaft receptacle is advantageously arranged in the pump housing for receiving a drive shaft of a drive motor associated with the motor housing. In this case, a partial chamber is arranged on the shaft receptacle and a line connection is provided on the underside of the partial chamber, relative to the mounting position of the hydraulic unit, from the partial chamber to the contact side. By means of the line connection, the leakage hydraulic fluid, which is normally accumulated in the eccentric chamber, can be guided out of the pump housing in a targeted manner on the contact side of the pump housing. The eccentric chamber forms a space in the pump housing, at which space the pump piston of the at least one pump element is supported on an eccentric bearing surrounding the drive shaft. The eccentric chamber is thus the pump outer space in which hydraulic fluid accumulates, which hydraulic fluid flows out of its pump inner space as leakage fluid during operation of the individual pump elements. In the case of a pump housing, which is preferably designed as a hydraulic block, the line connection is complicated in terms of manufacturing technology, in particular by a connection bore.

The invention also relates to the use of such a pump housing in a hydraulic unit of a vehicle brake system. In this case, a motor housing is additionally provided, which is mounted on a contact side of the pump housing, a separating element is provided between the contact side and the motor housing, with which a space is separated from the environment between the contact side and the motor housing, and a leakage chamber for receiving leakage fluid is formed between the separating element, the motor housing and the pump housing in the case of abutment with the second or third housing section.

The separating element is preferably designed as a hydraulic fluid-tight structure in this case or is additionally provided with a sealing element in such a way that the leakage space is sealed off from the environment of the hydraulic assembly in order to prevent leakage of hydraulic fluid. The separating element is preferably designed as a connecting and separating element by means of a motor flange, with which the motor housing is mounted in a stationary manner on the contact side of the pump housing or is connected to the pump housing. It is particularly preferred if the separating element is a part of the motor housing, in particular a longitudinal wall of the motor housing extending parallel to the motor axis or an already described excess of the longitudinal wall. The excess is realized by means of a transverse wall extending transversely to the longitudinal wall in the interior of the motor housing. The transverse wall is preferably a partial wall, in the center of which an opening for a further functional element of the drive motor is provided.

Undesirable hydraulic fluid leakage occurs in particular during operation of the hydraulic assembly as a result of the sealing elements in or on the pump element not sealing completely. Hydraulic fluid flowing out of the pump element as leakage fluid is first discharged into the eccentric chamber. In the eccentric chamber, the leakage fluid first occurs during operation when the eccentric bearing and the drive shaft arranged there rotate. According to the invention, the leakage fluid can now advantageously be conducted from the eccentric chamber to the contact side of the pump housing by means of a line connection and is received there in the leakage chamber according to the invention.

In the case of an abutment with the second or third housing section, the leakage chamber according to the invention is formed between the separating element, the motor housing and the pump housing and is therefore particularly large. The pump housing requires only a few spatial positions in the spatial direction on the second or third housing section compared to the first housing section, since the second and third housing thicknesses are smaller than the first housing thickness. This undesired spatial position is used for the leakage chamber by means of a motor housing and a separating element which are mounted on the contact side. Thus, according to the invention, the leakage space is particularly large compared to known pump housings having a uniform housing thickness. For such pump housings, two leakage holes are usually provided in the hydraulic block on the contact side, with which conventional leakage spaces are provided. According to the invention, such leakage holes can be dispensed with. In this way, a hydraulic assembly with reduced variability can be produced in the pump housing particularly easily and cost-effectively in terms of production technology. A single leakage scheme is provided for all pump housing types in a hydraulic assembly. In addition, the leakage chamber according to the invention does not require an increase in the volume of the hydraulic unit despite the large leakage space. No additional installation space is consumed in the vehicle brake system.

Furthermore, when the pump housing according to the invention is used in a hydraulic unit, the fuel consumption of the associated motor vehicle can be reduced by virtue of the weight saving on the pump housing. Less harmful substances are emitted and the carbon dioxide balance of the motor vehicle is improved.

According to the invention, a motor housing recess is advantageously provided in the motor housing adjacent to the second or third housing section, with which additional leakage chambers are provided. An additional space is formed on the motor housing side between the motor housing, the partition element and the second or third housing section by means of the motor housing recess. With the additional space, in combination with the smaller second or third housing thickness, the leakage chamber formed by it can be expanded without having to enlarge the hydraulic assembly volume.

Drawings

Embodiments of the solution according to the invention are explained in detail below with reference to the schematic drawing. Wherein:

FIG. 1 illustrates a front view of a conventional pump housing;

FIG. 2 shows a view according to II shown in FIG. 1;

FIG. 3 shows a cross-sectional view III-III according to FIG. 1;

fig. 4 shows an oblique view according to fig. 1 with the motor housing installed;

fig. 5 shows a view according to fig. 1 of a first exemplary embodiment of a pump housing according to the invention;

fig. 6 shows a view according to VI shown in fig. 5;

FIG. 7 shows an oblique view of the first embodiment according to FIG. 5;

fig. 8 shows an oblique view with the motor housing installed according to fig. 5;

FIG. 9 shows a cross-sectional view IX-IX according to FIG. 8;

FIG. 10 shows a detail according to X shown in FIG. 9;

fig. 11 shows a detail X according to fig. 9 of a third exemplary embodiment of a hydraulic assembly according to the present disclosure; and is

Fig. 12 shows an oblique view of a second exemplary embodiment of a pump housing according to the invention.

Detailed Description

Fig. 1 to 5 partially show a hydraulic unit 10 of a vehicle brake system, which is not further shown. The hydraulic unit 10 comprises a hydraulic block as a block-shaped pump housing 12, which is produced from an extruded profile by means of an extrusion process or an extrusion process. In the block-shaped pump housing 12, functional boreholes are provided, of which only the most important boreholes are identified for the sake of simplicity.

In addition to the pump housing 12, the hydraulic unit 10 also comprises a drive motor, not shown, which is accommodated in a cup-shaped motor housing 14 and is supported there. The motor housing is mounted or arranged in a fluid-tight and positionally fixed manner relative to its cup bottom 16 on a contact side 18 on the pump housing 12. For this purpose, a fluid-tight connection flange or motor flange 20 is provided on the motor housing 14, which has at least two fastening brackets 22 extending parallel to the contact side 18. The motor housing 14 is fixed in position to the pump housing 12 by means of screws, not shown, by means of individual fastening brackets 22.

Two pump receptacles 26, each of which is designed as a stepped bore with a pump receptacle axis 28, are provided in the pump housing 12, diametrically opposite to the motor axis 24 associated with the motor housing 14. The pump receptacle axis 28 extends parallel to the contact side 18. In the center of the two pump receptacles 26, a blind-hole-like bore is provided, which serves as a shaft receptacle 30 with an end 32 that is open toward the contact side 18. The shaft receptacle 30 extends with its shaft receptacle axis 34 perpendicular to the pump receptacle axis 28. The shaft receptacle 30 comprises a receptacle end region 36, in which the drive shaft, not shown, is to be received at one end of the drive shaft assigned to the drive motor. The drive shaft is supported in the motor housing 14 at its other end. Furthermore, the shaft receptacle 30 comprises an eccentric region or eccentric chamber 38, in which an eccentric bearing, not shown, is intended to be arranged around the drive shaft. In parallel to the shaft receptacle axis 34, two transverse bores 40 are provided in the pump housing 12 on each pump receptacle 26, into which transverse bores 40 solenoid valves for regulating the brake fluid flow are to be received (fig. 3).

The pump housing 12 has a square shape with an edge length in the spatial direction 42 corresponding to the housing thickness 44. The housing thickness 44 remains of the same design over the entire pump housing 12 and thus also forms the almost flat contact side 18. Two blind-hole-shaped leakage boreholes 46 are provided on the contact side 18, with which leakage spaces can be provided in the case of the installation of the motor housing 14. In particular, brake fluid which accumulates there as leakage fluid during operation of the hydraulic unit 10 flows out of the eccentric chamber 38 into this leakage space. Fig. 1 shows such a leakage flow 48 from a pump element, not shown, which is assigned to one of the two pump receptacles 26. A similar leakage flow applies for the opposite pump element.

According to fig. 4, the motor housing 14 is mounted on the pump housing 12, thereby forming a standard package 50 having a standard package thickness 52 extending in the spatial direction 42. Fig. 4 furthermore shows the standard component 50 and thus the assembly position 54 of the hydraulic aggregate 10.

Fig. 5 to 12 show a hydraulic assembly 10 in part, which, in contrast to a pump housing 12 having a constant housing thickness 44, has a pump housing 56 that comprises a first housing section 58 having a first housing thickness 60, a second housing section 62 having a second housing thickness 64, and a third housing section 66 having a third housing thickness 68. In this case, the first housing thickness 60 is greater than the second housing thickness 64 and the third housing thickness 68. The third housing thickness 68 is as large as the second housing thickness 64. Furthermore, the third housing section 66 is arranged opposite the second housing section 62 with respect to the first housing section 58.

Two pump receptacles 26 are arranged in the first housing section 58 radially and perpendicularly to the shaft receptacle 30. Furthermore, the associated transverse bore 40 is accommodated in the first housing section 58. Fig. 3 shows a corresponding sectional view, and fig. 3, although referring to a pump housing 12 with a housing thickness 44 that remains the same, also applies to the first housing section 58 of the pump housing 56 according to the invention. The first housing thickness 60 is here as large as the housing thickness 44 of the known pump housing 12.

The

different housing thicknesses

60, 64 and 68 are formed on the pump housing 56 in such a way that an outer surface 70 of the pump housing 56 has two transitions 72. There is a first transition 72 from the first housing section 58 to the second housing section 62 and a second transition 72 from the first housing section 58 to the third housing section 66. The two transitions are provided here with respectively equally high, slightly chamfered steps 74. For this purpose, the pump housing 56 has been produced from an extruded profile by means of an extrusion method and a die, which is correspondingly formed in the shape of a step, in the extrusion direction of the extruded profile. The pump housing 56 is thus designed in the form of a block as a hydraulic block. The hydraulic block has a reduced disk thickness by virtue of the second and

third housing thicknesses

64 and 68 being smaller than the central region of the first housing section 58.

The outer surface 70 of the pump housing 56 represents a contact side 76 for mounting the drive motor with its motor housing 14. For this purpose, a recess 78 is milled into the contact side 76 of the first housing section 58. The recess 78 is in its cross section configured as a part of a circular ring having an outer circumference 82 and an inner circumference 84, which are spaced apart from one another by a distance 85. Furthermore, the recess 78 is positioned concentrically to the motor axis 24 of the motor housing 14 to be mounted and thus also concentrically to the shaft receptacle axis 34. The recess 78 has a first base surface 86 on the contact side 76 by means of a distance 85. Furthermore, a second bottom 88 of the second housing section 62 and a third bottom 90 of the third housing section 66 are provided on the contact side 76. Here, the first, second and third bottom surfaces 86, 88 and 90 form a flat contact surface 92, to which contact surface 92 the motor housing 14 is to be attached.

Fig. 8 depicts the motor housing 14, which is attached to the flat contact surface 92 by means of the connecting flange 20, in dashed lines and in perspective without structural elements in the motor housing 14 for greater clarity. An air-filled free space or space 94 is provided between the motor housing 14 and the second bottom 88 of the second housing section 62 and the third bottom 90 of the third housing section 66, respectively. The space 94 is separated in a fluid-tight manner from the environment 98 by a separating element 96. The space 98 located below with respect to the mounting position 55 can be used as a leakage chamber 100 together with the partition element 96, the part of the second bottom surface 88 enclosed by the partition element 96 and the motor housing 14.

By means of the leakage chamber 100, leakage brake fluid which has accumulated in the eccentric chamber 38 and which has flowed out of the pump element can be accommodated. For this purpose, connection openings are provided as line connections 104 in the lower side 102 or in the lower region of the partial chamber 38 relative to the mounting location 54. By means of the line connection 104, the leakage fluid is guided from the deviating chamber 38 up to the second bottom 88 of the contact side 76 and is received there by the leakage chamber 100.

This leakage chamber 100 is used to provide a much greater amount of leakage than is provided by means of the two leakage holes 46. In addition, the standard cell 106 formed with the pump housing 56 and the motor housing 14 has a standard cell thickness 108 that is as great as the standard cell thickness 52. This provides an enlarged leakage space 100, which does not require additional space in the hydraulic unit 10. The volume of the hydraulic assembly does not need to be enlarged.

The spacer element 96 is provided here with a fluid-tight connecting flange 20 and an excess portion 110 as part of the motor housing 14 itself. For this purpose, the cup-shaped motor housing 14 has a hollow cylindrical longitudinal wall 112 extending parallel to the motor axis 24 and adjoining at one end 114 thereof to the cup bottom 16 extending transversely thereto. A transverse wall 116 extending transversely to the cup bottom 16 is enclosed by the longitudinal wall 112 and is arranged so as to be displaced in the interior of the motor housing. With such a displaced arrangement, the excess portion 110 of the longitudinal wall 112 is formed between the other end 118 of the longitudinal wall 112 and the lateral wall 116. The transverse wall 116 is designed as a partial wall which has an opening 120 radially on the inside, in which functional elements of the drive motor, not shown, can be arranged. In particular, the drive shaft, the axial bearing or a-bearing surrounding the drive shaft, and the associated a-bearing cover, which is usually sealed with a silicone seam, are arranged there. The a-bearing cap is preferably also part of the transverse wall 116.

Fig. 11 shows an embodiment in which the transverse wall 116 is provided with a step 122 which projects into the interior of the motor housing 14. A motor housing recess 124 is thereby formed adjacent to the second bottom surface 88 of the second housing section 62, which enlarges the leakage chamber 100.

Fig. 12 shows an embodiment in which the recess 78 is provided in its cross section with a part of a ring 80, the spacing 85 between the inner circumference 84 and the outer circumference 82 of which is greater than in the embodiment according to fig. 7. In this case, the motor housing 14 is arranged with its spacer elements 96 almost without a distance on the outer circumference 82 and with a correspondingly larger distance on the inner circumference 84. With such a design of the recess 78, material on the first housing section 58 can additionally be saved. According to fig. 7 and 12, a material region 126 that is thickened compared to the recess 78 is present radially on the inside and a correspondingly thickened material web 128 is present radially on the outside. Both the material region 126 and the material web 128 have the first housing thickness 60. The material region 126 thus provides, in particular, sufficient space for the shaft receptacle 30 and sufficient material for stably stamping the axial bearing required there. By means of the material webs 128, sufficient material is present for making it possible to punch the pump element into the pump receptacle 26.

Claims

1. A pump housing (56) of a hydraulic assembly (10) of a vehicle brake system, having a first housing section (58) and a second housing section (62) and at least one pump receptacle (26) for receiving a pump element,

characterized in that the at least one pump receptacle (26) is arranged in the first housing section (58) and the first housing section (58) has a first housing thickness (60) and the second housing section (62) has a second housing thickness (64), wherein the second housing thickness (64) is smaller than the first housing thickness (60).

2. The pump housing according to claim 1,

characterized in that a third housing section (66) is provided, which is arranged opposite the second housing section (62) with respect to the first housing section (58), the third housing section (66) having a third housing thickness (68) and the third housing thickness (68) likewise being smaller than the first housing thickness (60).

3. The pump housing according to claim 1 or 2,

characterized in that the pump housing (56) has an outer surface (70) which is provided with a transition (72), in particular with a step (74), from the first housing section (58) to the second housing section (62) and/or to the third housing section (66).

4. The pump housing according to claim 3,

characterized in that the outer surface (70) provided with the transition (72) is a contact side (76) of the pump housing (56) for mounting a motor housing (14).

5. The pump housing according to claim 4,

characterized in that, on a contact side (76) of the pump housing (56), the first housing section (58) is provided with a recess (78) in which the motor housing (14) is partially arranged.

6. The pump housing according to claim 5,

characterized in that the recess (78) of the first housing section (58) is provided with a first bottom surface (86), the second housing section (62) is provided with a second bottom surface (88) on the contact side (76) of the pump housing (56), and/or the third housing section (66) is provided with a third bottom surface (90) on the contact side (76) of the pump housing (56), wherein a flat contact surface (92) for mounting the motor housing (14) is formed together with the first and second bottom surfaces (86, 88) and/or the third bottom surface (90).

7. The pump housing according to claim 5 or 6,

characterized in that the recess (78) has the shape of a portion of a circular ring (80) in its cross section, and the circular ring (80) is arranged in particular concentrically to the motor axis (24) of the motor housing (14) to be mounted.

8. The pump housing according to claim 7,

characterized in that a part of the ring (80) is provided with an outer circumference (82) and an inner circumference (84), wherein the motor housing (14) is arranged in the recess (78) almost without a distance on the outer circumference (82) and at a distance from the inner circumference (84).

9. The pump housing according to any one of claims 4 to 8,

characterized in that a shaft receptacle (30) is arranged in the pump housing (56) for receiving a drive shaft of a drive motor associated with the motor housing (14), a partial chamber (38) is arranged on the shaft receptacle (30), and a line connection (104) extending from the partial chamber (38) up to the contact side (76) is provided on the underside (102) of the partial chamber (38) in relation to the installation position (54) of the hydraulic assembly (10).

10. Use of a pump housing (56) according to any of claims 1 to 9 in a hydraulic assembly (10) of a vehicle brake device,

characterized in that a motor housing (14) is furthermore provided, the motor housing (14) is mounted on a contact side (76) of the pump housing (56), a separating element (96) is provided between the contact side (76) and the motor housing (14), a space (94) is separated between the contact side (76) and the motor housing (14) relative to the environment (98) by means of the separating element, and a leakage chamber (100) is formed between the separating element (96), the motor housing (14) and the pump housing (56) when the second housing section (62) or the third housing section (66) is in abutment.