Hydraulic unit

Abstract

Hydraulic unit (10), in particular for a slip-controlled vehicle braking system, with a housing block (52), a pump receptacle (50) formed on the housing block (52) and aligned along a longitudinal axis (L) for receiving a pump (30) with a pump suction side and a pump discharge side, and a first fluid channel (80) crossing the pump receptacle (50) in the area of ​​the pump discharge side. a second fluid channel (82) opening into the pump housing (50) in the area of ​​the pump pressure side, a first separation point (100) formed between the openings of the two fluid channels (80, 82) into the pump receptacle (50), which seals the two fluid channels (80, 82) against each other and a damper arranged on the housing block (52), into which the first fluid channel (80) and the second fluid channel (82) open, characterized by, that the damper has a damper receptacle (90) for a damper element (44) which forms a second separation point (102) with the damper receptacle (90) which seals the two fluid channels (80, 82) against each other, wherein the first fluid channel (80) connects a switching valve (24) with an inlet valve (18) of a brake circuit of a vehicle brake system, is free of throttling points and directs pressure medium at least sectionally around an assembly component (68; 54) and wherein a pressure side of the pump (30) opens into the second fluid channel (82) and the second fluid channel (82) is connected to the damping element (44).

Description

State of the art

[0001] The invention relates to a hydraulic unit, in particular for a slip-controllable vehicle braking system according to the features of the preamble of claim 1.

[0002] Such a hydraulic unit is disclosed in DE 103 02 681 B3. The known hydraulic unit has damping devices whose installation spaces extend toward a mounting surface of the housing block, to which an electronic control unit can be attached. The damping devices protrude beyond this mounting surface.

[0003] Piston pumps which are installed in pump housings of hydraulic units are also known from DE 103 14 979 B3 or DE 10 2011 089 984 A1.

[0004] Another hydraulic unit is known, for example, from DE 10 2008 002 740 A1. This known hydraulic unit has a housing block on which the individual components for regulating the brake pressure depending on the existing wheel slip are arranged and hydraulically connected to one another. A key component for this is a pump, which is inserted into a pump receptacle of the housing block and is actuated, for example, mechanically by an electric motor and an eccentric driven by it. Pumps convey pressure fluid away from the wheel brakes when needed to reduce the wheel brake pressure or provide the wheel brakes with high-pressure pressure fluid if an increase in the wheel brake pressure is necessary.

[0005] Piston pumps, in particular, can trigger pressure pulsations due to their cyclical operating principle, which can be perceived as undesirable operating noise in the vehicle. To smooth or dampen these pulsations, damping devices are provided on the pump pressure side. These devices usually comprise at least one pressure fluid accumulator with a pressure-dependently variable storage capacity (C element) and at least one throttle element (R element) arranged downstream of it. Examples of pressure fluid accumulators include spring-actuated piston accumulators, which are arranged in a dedicated accumulator receptacle of the hydraulic unit and are connected to the pump pressure side via fluid channels carrying pressure fluid. Throttle elements include fixed throttles with a constant throttle cross-section or dynamic throttles with a pressure-dependently variable throttle cross-section.

[0006] Regardless, due to the limited space available in motor vehicles, it is necessary to design the hydraulic unit and thus its housing block as compact and lightweight as possible. A common measure for this is to arrange the fluid channel for contacting a switching valve with an inlet valve of a vehicle brake system on the hydraulic unit in such a way that it crosses a pump intake.

[0007] If a damping device is connected to a fluid channel arranged in this way to dampen pressure pulsations, the disadvantage arises that the throttle element downstream of the accumulator represents a flow resistance, which has a detrimental effect in operating conditions of the vehicle braking system in which the rapid provision of the largest possible pressure volume is essential. These include, for example, emergency braking, particularly to avoid a collision with other road users. Particularly with falling temperatures and the correspondingly increasingly viscous pressure medium, the throttling effect of the throttle element increases significantly, thus exacerbating the described effect. Advantages of the invention

[0008] In contrast, a hydraulic unit according to the features of claim 1 has the advantage that the pressure pulsations of a pump can be effectively reduced without the measures used for this purpose having a negative influence on the size of the building block or on the functional properties, in particular the pressure build-up dynamics, of the vehicle braking system.

[0009] According to the invention, among other things, a second fluid channel is provided, which opens into the pump receptacle in the area of ​​the pump pressure side. Furthermore, a separation point is provided to seal the two fluid channels from each other. The first fluid channel, which crosses the pump receptacle, flows around the pump inserted into the pump receptacle, while the second fluid channel contacts the pump pressure side with the pressure pulsation damper. Downstream of the pressure fluid accumulator, the two fluid channels are merged.

[0010] The sealing of the two fluid channels against each other can be achieved by modifying existing unit components and an adapted design of the building block, so that the overall number of components and the parts and assembly effort of the hydraulic unit are only insignificantly increased by the invention.

[0011] The pressure pulsation damper can be optimized for its actual function of damping pressure pulsations and thereby improving the operating noise of the vehicle brake system without negatively affecting its functional properties, in particular the pressure build-up dynamics.

[0012] Further advantages or advantageous developments of the invention emerge from the subclaims and / or from the following description.

[0013] Sealing the fluid channels from each other can be achieved particularly easily and cost-effectively if a closure element interacting with the housing block is used as the unit component to form the separation point. This closure element is already designed to seal the pump bore from the environment. Alternatively, a cylinder element of the pump, which is designed to guide a piston, can be used instead of the closure element.

[0014] The joint can be formed in a variety of ways through positive and / or frictional engagement between the housing block and the component, and can therefore be adapted to the specific application. In addition to a reliable and permanent sealing effect, a single operation simultaneously ensures a permanent anchoring of the respective component to the housing block.

[0015] The use of cutting edges on one or more components to be fastened together allows for the fixation to be achieved through an easy-to-control and simple-to-monitor press-in process, without the need for additional material or tools. Given the relatively small dimensions of the pump element, this is advantageous because it allows for at least partially automated assembly. The fluid channels are particularly space-saving and particularly easy to manufacture if they are aligned on the housing block essentially at right angles to a longitudinal axis of the pump mount and / or if they run axially parallel to each other at least in sections. drawing

[0016] Embodiments of the invention are illustrated in the figures and explained in detail in the following description. Fig. 1 shows, for the understanding of the technical background, a brake circuit of a slip-controllable vehicle brake system, which is equipped with the components essential to the invention; in Fig. 2 shows a first embodiment of the invention in a schematically simplified manner using a longitudinal section through a hydraulic unit in the region of the pump pressure side; Fig. 3 discloses a longitudinal section through a damper unit installed in the hydraulic unit; In the Fig. 4 and Fig. 5 are second and third embodiments of the invention, also shown in longitudinal section. The Fig. 6 shows the housing block with a pump installed in a pump receptacle in longitudinal section, wherein a first separation point between the fluid channels crossing the pump receptacle on the pump pressure side is further developed with regard to its sealing effect.

[0017] A second embodiment of a correspondingly developed first separation point discloses Fig. 7. Description of the implementation examples:

[0018] Fig. Figure 1 shows the hydraulic components of a brake circuit of a vehicle brake system using a hydraulic circuit diagram. These hydraulic components are partly connected indirectly to a hydraulic unit 10 or partly arranged directly on this hydraulic unit 10. The hydraulic unit 10 as such is shown as a dot-dash border line in Fig. 1 symbolically shown. A master brake cylinder 12 is connected to the hydraulic unit 10, which can be actuated by the driver via a brake pedal 14. Furthermore, two wheel brakes 16 are connected to the hydraulic unit 10, which are supplied with pressure medium from the hydraulic unit 10. To control the brake pressure depending on the current slip conditions at the wheels of a vehicle assigned to the wheel brakes 16, each wheel brake 16 is assigned a so-called pressure build-up or inlet valve 18 and a so-called pressure reduction or outlet valve 20. The inlet valves 18 are located in a pressure medium connection 22, which connects the connection of the master brake cylinder 12 on the hydraulic unit 10 to a connection of one of the wheel brakes 16 shown. A so-called changeover valve 24 is provided to control this pressure medium connection 22.If this interrupts the pressure medium connection 22 by electronic control, the master brake cylinder 12 is decoupled from the wheel brakes 16 and the driver cannot change the brake pressure on the wheel brakes 16 by muscle power.

[0019] The outlet valves 20 can be opened by electronic control to discharge pressure fluid from the wheel brakes 16 as needed when a reduction in the brake pressure becomes necessary. The outflowing pressure fluid enters a return line 26 formed on the hydraulic unit 10 with a buffer reservoir 28 connected to it, which initially absorbs the outflowing pressure fluid. Downstream of the buffer reservoir 28, an externally driven pump 30 is connected, which pumps the pressure fluid from the buffer reservoir 28 and feeds it back into the pressure fluid connection 22 of the master brake cylinder 12 with the wheel brakes 16 via a pump pressure line 32 connected to the pump outlet. For this purpose, the pump pressure line 32 opens into this pressure fluid connection 22 in the section between the changeover valve 24 and the inlet valve 18.

[0020] Should the buffer reservoir 28 alone be insufficient to supply the pump 30 with pressure medium, a suction line 34 is provided on the hydraulic unit 22, which connects the suction side or pump inlet of the pump 30 with the connection of the master brake cylinder 12 on the hydraulic unit 10. This suction line 34 is controlled by demand-based electronic control of a so-called high-pressure switching valve 36.

[0021] This component arrangement and its interaction for regulating the brake pressure of the wheel brakes 16 are therefore state of the art.

[0022] Piston pumps are often used as pumps 30 in anti-slip vehicle brake systems. Their pistons are driven by an eccentric to reciprocate. This cyclical operation can cause pressure pulsations, which can be transmitted to the vehicle and perceived as operating noise or vibration.

[0023] To dampen pressure pulsations in a low pressure range up to approximately 40 bar, the pump pressure side interacts with a low-pressure damper 40, which is followed by a low-pressure throttle 42. The low-pressure damper 40 and the low-pressure throttle 42 together form a low-pressure damping device, which, together with the pump 30, can form a single assembly that can be arranged in a pump receptacle 50 of the hydraulic unit 10.

[0024] Furthermore, a high-pressure damper 44 is provided downstream of the low-pressure throttle 42 to dampen pressure pulsations in the high-pressure range, i.e., above approximately 40 bar. A high-pressure throttle is not visibly integrated into the high-pressure damper 44. Both components together form a high-pressure damping device. This is connected to the pressure fluid connection 22 leading from the connection of the master brake cylinder 12 to the connection of the wheel brakes 16, in the area between the changeover valve 24 and the inlet valves 18.

[0025] The invention consists in arranging the explained components for damping the pressure pulsations on the hydraulic unit 10 in the most space-efficient manner possible and in particular hydraulically in accordance with the Fig. 1, without impairing the functional properties, in particular the pressure build-up dynamics of the vehicle brake system. A first embodiment of this is shown in Fig. 2 shown.

[0026] Fig. Figure 2 shows a section of the outlet or pressure-side end of a pump 30 designed as a piston pump. This is installed in a pump receptacle 50 of the housing block 10. The pump receptacle 50 is open to the outside and is closed by a plug 68. A cylinder element 54 of the pump 30 takes up a Fig. 2 not visible piston and serves to guide it. The piston is actuated against the force of a return spring 56, which is supported on the bottom of the cylinder element 54. In the center of the bottom of the cylinder element 54 is a through-bore 58, which ends in a conical valve seat 60. This valve seat 60 is controlled by a closing member 62, here exemplary designed as a ball, which is pressed against the valve seat 60 by a valve spring 64. The valve spring 64 is supported at the bottom of a blind hole-shaped recess 66 in the plug 68. The latter is anchored in the pump receptacle 50 by means of a force-fitting press connection.

[0027] In the illustrated state, the closing member 62 rests against the valve seat 60 and thereby prevents pressure medium from escaping from the interior of the cylinder element 54 into the outlet or pressure area of ​​the pump 30. With a movement of the piston in Fig. 2 downwards, a pump chamber 70 enclosed by the piston and the cylinder element 54 decreases in size and the pressure inside the pump chamber 70 increases. If the hydraulic pressure force on the closing member 62 becomes greater than the counteracting spring force, the closing member 62 lifts off the valve seat 60 and pressure medium flows through the through-bore 58 to an annular groove 72, which is formed on an end face of the plug 68 facing the cylinder element 54. The annular groove 72 surrounds the valve seat 60 at a radial distance, whereby a circumferential web 74 is formed between the annular groove 72 and the valve seat 60. At least one radially extending recess is provided, which crosses the web 74 and can be designed as a throttle cross-section 76. Pressure medium flows through the throttle cross-section 76 to a fluid channel 82 formed in the housing block 52, which is referred to below as the second fluid channel 82 for reasons of confusion.The latter is arranged essentially at right angles to a longitudinal axis L of the pump holder 50 and opens into a non-recognizable damper holder 90 (. Fig. 3) on the housing block 52 of the hydraulic unit 10. The damper mount 90 accommodates the high-pressure damper element 44.

[0028] Furthermore, a so-called first fluid channel 80 is provided on the housing block 52 according to the invention, which is aligned at least partially axially parallel to the second fluid channel 82 and crosses the pump receptacle 50. This first fluid channel 80 connects according to Fig. 1 connects the changeover valve 24 of the vehicle brake system to the inlet valve 18 and thus forms the pressure medium connection 22. The first fluid channel 80 also runs at right angles to the longitudinal axis L of the pump receptacle 50, but unlike the second fluid channel 82, is free of throttle points and thus allows an unhindered flow of pressure medium from the changeover valve 24 to the inlet valve 18. For this purpose, the pump receptacle 50, together with the pump 30 inserted therein, forms an annular channel 84 surrounding the installed cylinder element 54 of the pump 30, into which annular channel 84 the first fluid channel 80 flows on one circumferential side of the pump receptacle 50 and flows out again on the opposite circumferential side.

[0029] According to the invention, the two fluid channels 80 and 82 are sealed from each other. This is achieved by means of a first separation point 100, which is formed by a housing section 104 of the pump receptacle 50 located between the two fluid channels 80 and 82 in operative connection with an assembly component inserted into the pump receptacle 50. In the illustrated embodiment, this assembly component is the plug 68, which closes the pump receptacle 50 from the environment.

[0030] Alternatively, the cylinder element 54 of the pump 30 could also be used as the unit component, but this will only be discussed below in connection with the description of Fig. 4 is revealed in detail.

[0031] The plug 68 and the cylinder element 54 of the pump 30 are mechanically coupled to one another, for example. To form this coupling, the plug 68 is provided with a collar 108 into which the cylinder element 54 is immersed until the two components abut one another with their respective end faces. In this area, the cylinder element 54 is provided with a circumferential, radially projecting collar 110, which the collar 108 projects beyond axially in the direction of the longitudinal axis L. After the cylinder element 54 and the plug 68 have been brought into contact with one another, the collar 108 is plastically deformed, whereby it engages behind the collar 110 of the cylinder element 54 and thus positively connects the two components to form an assembly.

[0032] This assembly, consisting of plug 68 and cylinder element 54, is inserted into the pump receptacle 50 until a chamfer 112 formed on the cylinder element 54 engages a counter-chamfer 114 of the pump receptacle 50, thereby sealing the pump pressure side from the pump suction side. The plug 68 has an oversize diameter compared to the diameter of the pump receptacle 50, so that a force-locking connection, i.e., a press connection, can be formed between the plug 68 and the pump receptacle 50. The press connection extends to the housing section 104 located between the two fluid channels 80 and 82 and thus forms the first separation point 100.

[0033] According to Fig. 3, the second fluid channel 82 opens at its end facing away from the pump receptacle 50 into a damper receptacle 90 formed on the housing block 52 for the high-pressure damper element 44. The opening point of the second fluid channel 82 is located eccentrically to a central axis M of the damper receptacle 90 in a region which allows unhindered flow around a supply valve 96 of the high-pressure damper element 44 installed in the damper receptacle 90. The latter is exemplarily equipped with a damper piston 92 which, acted upon by a damper spring 94, has a Fig. 4. In this basic position, the supply valve 96 of the damper device is opened by the damper piston 92 and thus establishes a pressure medium connection to the second fluid channel 82, which also opens into the damper receptacle 90. Pressure pulsations occurring in the second fluid channel 82 can be dampened by the mobility of the damper piston 92 against the force of the damper spring 94.

[0034] The supply valve 96 is equipped with a high-pressure throttle (not shown) through which the pressure medium contained in the high-pressure damper 44 flows. Downstream of this high-pressure throttle, the first fluid channel 80 and the second fluid channel 82 merge into one another. The supply valve 96 thus acts as a second separation point 102 for mutually sealing the two fluid channels 80 and 82.

[0035] A particularly effective force-locking connection of the unit component, or according to embodiment 1 of the plug 68, with the pump receptacle 50 can be achieved by shrinking the plug 68. For this purpose, the plug 68 is cooled before the pressing-in process to a temperature that is significantly lower than the temperature of the building block 52 in the area of ​​the pump receptacle 50. With its subsequent heating, the radial clamping forces acting on the plug 68 increase to a magnitude that, without cooling, would have required significantly higher axial pressing forces and thus increased the risk of undesirable chip formation.

[0036] Fig. 2 further shows that, if necessary, in addition to the press connection, the plug 68, and indirectly thus the pump 30, can be secured in the pump receptacle 50 by forming a caulking 116. For this purpose, the housing block 52 is plastically deformed in the circumferential region of the pump receptacle 50 by means of a stamp such that this material of the housing block 52 covers a shoulder 116 provided in the circumferential direction of the plug 68, at least in segments or sections.

[0037] Instead of the described purely force-locking connection between the unit component and the pump receptacle 50 to form the first separation point 100, a combination of a force-locking and a form-locking connection can alternatively be provided. Such a second embodiment is shown in Fig. 4 shown.

[0038] In this exemplary embodiment, the unit component or plug 68 is provided on its outer circumference with cutting edges 118 that extend axially or in the direction of the longitudinal axis L of the pump receptacle 50. The inner diameter of the pump receptacle 50 is recessed in sections at a step to such an extent that, when the plug 68 is joined, the cutting edges 118 cut into the wall of the recessed section of the pump receptacle 50. The number or grouping of cutting edges 118 distributed over the circumference of the plug 68 can be freely selected depending on the application.The cutting edges 118 secure the plug 68 in the pump receptacle 50 against rotation and thus form a positive connection, while in addition, when cutting into the section of the wall of the pump receptacle 50 which has a recessed inner diameter, they displace material laterally and thus increase the clamping forces acting on the plug 68 compared to the clamping forces achievable by pure force connection.

[0039] Another variant for representing the combination of a force-locking and a form-locking first separation point 100 is possible by using a so-called self-clinch connection between the pump holder 50 and the unit component. This variant shows Fig. 5. In this example, the cylinder element 54 of the pump 30 is used as the unit component. This consideration could, in principle, also be applied to the previously described design variants.

[0040] After Fig. 5, the cylinder element 54 is provided with annular, circumferential cutting edges 118 on its outer circumference. By way of example, two cutting edges 118 are formed, which come to lie on either side of the opening cross-section of the first fluid channel 80 into the pump receptacle 50 when the cylinder element 54 of the pump 30 is in its intended final press-in position. Several cutting edges 118 on either side of the opening cross-section of the first fluid channel 80 would of course be conceivable. Circumferential grooves 120 are formed along the circumference of the cylinder element 54 in the joining direction of the cylinder element 54, above the cutting edges 118. When the cylinder element 54 is joined into the pump receptacle 50, the annular cutting edges 118 displace material from the wall of the pump receptacle 50 into these grooves 120 and thus form the positive connection between the components.

[0041] In this embodiment, a relatively flat cover 122 is used to close the opening of the pump receptacle 50, which cover can also be anchored in the pump receptacle 50 in a force-fitting and / or form-fitting manner.

[0042] The Fig. 6 shows an embodiment with a pump 30 that is inserted into a pump receptacle 50 of a housing block 10. According to the previously described examples, two fluid channels 80, 82 are formed in the housing block 10, which cross the pump receptacle 50 in the area of ​​the pump pressure side, with a first separation point 100 located between the two fluid channels 80, 82, at which the fluid channels 80, 82 are sealed against each other. According to the example according to Fig. 4, this first separation point 100 is formed by the cylinder element 54 of the pump 30 and by the wall of the pump receptacle 50 in the housing block 10, wherein the pump receptacle 50 is closed to the outside by a plug 68 which receives a valve spring 64 and a closing member 62 of an outlet valve of the pump 30 in a blind hole-like recess 66.

[0043] To improve the sealing effect of the first separation point 100, an additional sealing device 130 is provided thereon. In the embodiment according to Fig. 6, this sealing device 130 is a sealing ring 132, which is designed as a conventional O-ring. Alternatively, the use of a profile sealing ring or a spring sealing ring or the like would also be conceivable. The sealing ring 132 is received in a circumferential groove 134, which is formed on the cylinder element 54 for this purpose to simplify the assembly of the sealing ring 132, but could instead also be formed as a recess in the wall of the pump receptacle 50. The sealing ring 132 itself can be made of a fluid-resistant and permanently elastic elastomer, a thermosetting plastic, or a metal-plastic composite material.

[0044] O-rings made of elastomer are commercially available and accordingly inexpensive components which, due to their elastic properties, maintain their sealing effect even under changing temperature and pressure conditions, are easy to install and through their use the frictional connection between pump 30 or cylinder element 54 and pump holder 50 can be adjusted in such a way that the pump 30 can be dismantled and replaced with a spare part in the event of a possible defect.

[0045] The further embodiment according to Fig. 7 shows a pump 30 in a pump receptacle 50 of a housing block 10, this pump receptacle 50 crossing fluid channels 80, 82 as well as a first separation point 100 with improved sealing effect between the opening points of these fluid channels 80, 82 in the pump receptacle 50. However, in this example, the provided additional sealing device 134 is not a separate component as in the example according to Fig. 6, but as a sealing caulking 136, which is arranged in the region of the first separation point 100. This sealing caulking 136 is produced by a plastic deformation of material of the cylinder element 54 and / or the housing block 10 with the aid of a Fig. 7 not shown tool or punch. Corresponding sealing caulking 136 is in the Fig. 7 shown only schematically. A circumferentially open recess or groove 134 can be provided on the housing block 10 and / or on the cylinder element 54, into which the plastically deformed material penetrates, so that in addition to the already existing force connection or press connection between the cylinder element 54 and the pump receptacle 50, an additional form fit is formed between these structural units, which improves the sealing effect at the separation point 100.

[0046] Of course, further changes or additions to the described embodiments are conceivable without deviating from the basic idea of ​​the invention.

Claims

[1] Hydraulic unit (10), in particular for a slip-controllable vehicle brake system, with a housing block (52), a pump receptacle (50) formed on the housing block (52) and aligned along a longitudinal axis (L) for receiving a pump (30) with a pump suction side and a pump pressure side, a first fluid channel (80) crossing the pump receptacle (50) in the region of the pump pressure side, a second fluid channel (82) opening into the pump receptacle (50) in the region of the pump pressure side, a first separation point (100) formed between the opening points of the two fluid channels (80, 82) into the pump receptacle (50), which seals the two fluid channels (80, 82) against each other and a damper arranged on the housing block (52), into which the first fluid channel (80) and the second fluid channel (82) open, characterized by , that the damper has a damper receptacle (90) for a damper element (44), which forms a second separation point (102) with the damper receptacle (90), which seals the two fluid channels (80, 82) against each other, wherein the first fluid channel (80) connects a changeover valve (24) to an inlet valve (18) of a brake circuit of a vehicle brake system, is free of throttle points and guides pressure medium at least in sections around an aggregate component (68; 54) and wherein a pressure side of the pump (30) opens into the second fluid channel (82) and the second fluid channel (82) is connected to the damper element (44). [2] Hydraulic unit according to claim 1, characterized bythat the pump receptacle (50) forms a housing section (104) in the axial direction of its longitudinal axis (L) between the two fluid channels (80, 82), which, in interaction with the unit component (68; 54) inserted into the pump receptacle (50), forms the first separation point (100) between the two fluid channels (80, 82). [3] Hydraulic unit according to claim 1 or 2, characterized by , that the unit component is a plug (68) which closes the pump receptacle (50) to the environment or that the unit component is a cylinder element (54) which guides a piston of the pump (30). [4] Hydraulic unit according to one of claims 1 to 3, characterized by that at least the first separation point (100) is designed by frictional connection and / or by positive connection of the unit component (68; 54) with the pump receptacle (50) of the housing block (52). [5] Hydraulic unit according to claim 4, characterized bythat the frictional connection is established by pressing or shrinking the unit component (68; 54) into the pump receptacle (50). [6] Hydraulic unit according to claim 4 or 5, characterized by that the force and / or form fit of the aggregate component (68; 54) in the pump receptacle (50) is produced by at least one cutting edge (118) on the aggregate component (68; 54) and / or on the wall of the pump receptacle (50), said at least one cutting edge (118) plastically deforming material of the wall of the pump receptacle (50) and / or of the aggregate component (68; 54) when the aggregate component (68; 54) is inserted into the pump receptacle (50). [7] Hydraulic unit according to one of claims 4 to 6, characterized byin that the force-fit and / or form-fit connection of the unit component (68; 54) in the pump receptacle (50) is produced by at least one annular circumferential cutting edge (118) and an annular circumferential groove (120) arranged downstream of this cutting edge (118) on the unit component (68; 54) and / or on the pump receptacle (50), wherein the at least one cutting edge (118) presses material of the wall of the pump receptacle (50) and / or of the unit component (68; 54) into the groove (120) when the unit component (68, 54) is inserted into the pump receptacle (50). [8] Hydraulic unit according to one of claims 1 to 7, characterized by that at least one additional sealing device (130) is provided at the first separation point (100). [9] Hydraulic unit according to claim 8, characterized bythat the additional sealing device (130) has a sealing ring (132), in particular an O-ring, a profile ring or a spring sealing ring, which preferably consists of elastomer, thermoset or a metal-plastic composite material. [10] Hydraulic unit according to claim 8, characterized by that the additional sealing device (130) is a sealing caulking (136) which is produced by plastic deformation of material of the housing block (10) and / or a cylinder element (54). [11] Hydraulic unit according to claim 10, characterized by that plastically deformed material penetrates into a groove (134) formed in the region of the first separation point (100) on the housing block (10) and / or on the cylinder element (54).

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