Hydraulic module, in particular for pressure generation and / or pressure regulation in slip-controlled braking systems of motor vehicles, and assembly method for a hydraulic module

Abstract

The present invention relates in one aspect to a hydraulic module (10), in particular for pressure generation and / or pressure regulation in slip-controlled braking systems of motor vehicles, and further to an assembly method for the hydraulic module (10). The hydraulic module (10) comprises, inter alia, a piston pressure generator (14) having a piston (18) slidably accommodated in a cylinder bore (20) of a housing block (12) and drivable for an axial movement A. The piston (18) defines a working chamber (22) which changes its volume depending on the direction of movement of the piston (18). A guide gap (38) between the circumferential surface of the piston (18) and the cylinder bore (20) is sealed towards the working chamber (22) by a seal assembly (40a). The invention proposes a guide element (46) on the side of the seal assembly (40a) facing away from the working chamber (22), on which the piston (18) can be supported radially by its circumferential surface, the guide element (46) being received in a receiving groove (44) of the housing block (12) so as to project radially into the guide gap (38) at a section. The guide element (46) prevents the piston (18) from coming into contact with the wall of the cylinder bore (20) and thus prevents wear. In another aspect, the invention relates to an assembly method for the proposed hydraulic module.

Description

[Technical field]

[0001] The invention relates to a hydraulic module according to the features of the preamble of claim 1, in particular for pressure generation and / or pressure regulation in slip-controlled braking systems of motor vehicles, as well as to an assembly method for a hydraulic module according to the features of the preamble of claim 8.

[0002] A hydraulic module according to the invention is understood below to mean an assembly consisting of a housing block, a piston pressure generator arranged in the housing block and a transmission mechanism for driving the piston pressure generator.

[0003] The piston pressure generator has a piston, which is slidably accommodated in a cylinder bore of a housing block and defines a working chamber. The piston can be driven for axial movement in the pressure increase or pressure decrease direction by a transmission. The volume of the working chamber decreases when the piston is moved in the pressure increase direction or increases when the piston is operated in the pressure decrease direction opposite to the pressure increase direction. An electrically operable electric motor is used as the drive for the piston, which has a motor shaft, the rotational movement of which is converted into an axial movement of the piston by a transmission. The pressure medium displaced from the working chamber is displaced into a brake circuit which is connected to the hydraulic module, so that the pressure level prevailing in the brake circuit increases. In the opposite case, the pressure level decreases when the piston is operated in the opposite direction and the volume flows back from the brake circuit to the working chamber.

[0004] Preferably, in an electronically slip-controllable vehicle braking system, a hydraulic module of this kind is used to generate and / or regulate the brake pressure, which inter alia allows the brake pressure of the wheel brakes to be quickly and reliably adapted to the slip ratio of the assigned wheels of the vehicle or allows brake pressure boosting when the vehicle is in an unstable driving state or when the traffic situation around the vehicle requires this boosting in order to avoid an accident.

[0005] The operation of the piston pressure generator is controlled by an electronic control device and can be performed whether or not the driver of the vehicle desires to brake. Because the driver has no direct involvement in the brake pressure buildup, this type of braking system is called a non-human (external force) braking system, as opposed to a conventional human (muscle) braking system.

[0006] The piston of the piston pressure generator is, as described above, slidably accommodated in a cylinder bore of a housing block, the guide gap between the peripheral surface of the piston and the wall of the cylinder bore being sealed against the working chamber by a seal assembly. [Background technology]

[0007] One hydraulic module according to these configurations is already known, for example from US Pat. No. 5,399,633.

[0008] In the known hydraulic module, the guide gap between the cylinder bore and the piston circumference is designed to be relatively narrow, which has the advantage that this guide gap, and thus the working chamber, is well sealed and there is an extremely low risk that the seal assembly will be pushed into this guide gap as a result of the piston movement and thus be damaged.

[0009] However, it can be easily understood that the production of narrow guide gaps is, from a manufacturing technology point of view, more laborious and therefore more expensive than the production of wider guide gaps. In addition, dimensional deviations due to manufacturing tolerances of the piston, the bore and / or the transmission components can lead to concentricity errors of the longitudinal axes of these components, angular errors and / or wobbling movements of the driven piston. In connection with narrow guide gaps, these errors can lead to the walls of the bore coming into contact with the piston and thus being loaded and worn by the acting radial forces.

[0010] Certainly, measures can be taken against such wear, for example by suitable coating of the cylinder bores, but such coatings represent additional expenditure and have a negative impact on the production costs of the hydraulic module. Furthermore, these boundary conditions have an impact on the structural design, the manufacturing method and the choice of material for the pistons. [Prior art documents] [Patent documents]

[0011] [Patent Document 1] DE 102019208397 Summary of the Invention Effect of the Invention

[0012] The hydraulic module according to the features of claim 1 has the advantage that it can be manufactured more cost-effectively than conventional hydraulic modules, while the quality of the piston guiding and of the sealing of the working chamber or the guide gap for the piston remains unchanged. The cost savings are due, on the one hand, to the fact that the guide gap between the circumference of the piston and the wall of the bore can now be made wider in the radial direction, and, on the other hand, to the fact that it is possible to avoid the need for a costly coating of the wall of the bore and / or the circumference of the piston to prevent possible wear. In addition, it is possible to expand the possibilities in the selection of materials for the piston. For example, in the future it will be possible to use pistons made of steel, which can further be manufactured more cost-effectively by forming processes. The components of the power train are also now manufactured with sufficient quality by deep-drawing technology.

[0013] The mentioned advantages are based on the use of a guide element for the piston, which is arranged in a receiving groove on the housing side of the seal assembly facing away from the working chamber, which is formed along the inner circumferential surface of the cylinder bore and receives the guide element in such a way that it projects in a section into the guide gap between the piston circumferential surface and the cylinder bore.

[0014] Further advantages or advantageous developments of the invention can be seen from the dependent claims or the following description.

[0015] If a shape-resilient ring with obliquely slotted ends facing each other is used as the guide element, a radial preload is easily applied to the guide element during assembly, and its outside diameter is reduced. With the aid of an assembly sleeve and a punch, the guide element can thus be introduced into the cylinder bore and placed in the provided receiving groove without risk of damage. As soon as the guide element snaps into the provided receiving groove, it is held or restrained there in a fixed position after assembly of the piston in the cylinder bore.

[0016] Due to the acceptable costs, good friction properties and resistance to brake fluids, guide elements made in particular of PTFE are preferred.

[0017] The guide elements are accommodated in the receiving grooves so as to be movable in the axial and radial directions, and due to the slotted design, in conjunction with the shape elasticity of the guide elements, tolerance-induced wobbling movements of the piston, angular errors between the components of the piston drive or axial misalignments can be compensated for. Contact of the piston with the walls of the cylinder bore is largely eliminated.

[0018] The receiving grooves of the guide elements are stepped from the outside to the inside, so as to form abutment shoulders against which the guide elements can be supported in the radial direction. These abutment shoulders limit the maximum possible expansion of the guide elements and thus protect the components from impermissibly high loads or damage. The maximum deformation of the guide elements is limited by the relative position of the abutment shoulders to the longitudinal axis L to such an extent that no contact occurs between the piston circumference and the bore wall over the operating time of the hydraulic module, or that the resulting radial forces, if any, do not cause appreciable wear of the bore wall or the piston.

[0019] The smaller section of the receiving groove, as viewed in cross section, is located between the abutment shoulder and the groove bottom of the receiving groove. This section is hydraulically connected to the region of the housing which guides the pressure medium, so that the pressure medium flows to the rear surface of the guide element facing away from the piston and passes up to the piston circumference. In order to prevent the pressure medium from entering the inside of the transmission, the guide element is arranged in an advantageous development of the invention between two sealing assemblies. The sealing assemblies have pressure-actuable sealing lips which can be brought into contact with the groove flanks, the groove bottom or the housing block and the piston circumference by the effective pressure of the pressure medium. The sealing lips of the sealing assemblies are lubricated by the pressure medium present and are thus protected against premature wear. In addition, the lubricated sealing assemblies ensure a particularly effective sealing of the working chamber with minimal frictional forces which impede the piston movement.

[0020] An embodiment of the invention is illustrated in the drawing and is explained in more detail in the following description, which to this end comprises a number of figures. [Brief description of the drawings]

[0021] [Figure 1] FIG. 2 is a longitudinal sectional view of a hydraulic module according to the present invention. [Diagram 2] 2 is an enlarged view of the part X shown in FIG. 1, which shows the arrangement of guide elements in a housing block of a hydraulic module that is the basis of the invention; FIG. [Diagram 3] FIG. 2 is a diagram showing the assembly process of the guide element according to the present invention into the receiving groove of the housing of the hydraulic module, in an exploded three-dimensional view of the housing block, the assembly sleeve and the guide element. [Figure 4] FIG. 13 is a longitudinal cross-sectional view showing a section of a housing block with an assembly sleeve introduced into the cylinder bore and a guide element housed within the assembly sleeve, illustrating the assembly process of the guide element according to the present invention into the receiving groove of the housing of the hydraulic module. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0022] Corresponding components are designated by uniform reference numerals in the individual figures.

[0023] The hydraulic module 10 shown in Fig. 1 comprises a housing block 12 with a piston pressure generator 14 arranged therein. The hydraulic module 10 further comprises a transmission mechanism 16 for driving a piston 18 of the piston pressure generator 14. The housing block 12 defines a cylinder bore 20 in which a piston 18 is accommodated and movably guided for reciprocating axial movement, as indicated by the double arrow A. The piston 18 is configured as a hollow piston and defines, with its closed end or piston head, a working chamber 22 which is filled with a hydraulic pressure medium.

[0024] Arranged inside the hollow piston are the components of the transmission mechanism 16 which operate the piston 18. These components include a spindle 24 and a spindle nut 26 which surrounds the spindle 24. The spindle 24 is connected to the piston 18 at its end located inside the hollow of the piston 18 so as not to rotate relative to the piston 18. For this purpose, the spindle journal engages in a blind hole-shaped journal receiver on the inner surface of the piston head, thus forming a force connection between these components.

[0025] The outer circumferential surface of the spindle 24 and the inner circumferential surface of the spindle nut 26 are provided with mutually assigned, spirally surrounding rolling raceway sections of a ball circulation raceway, the balls accommodated in the ball circulation raceway forming a mechanical engagement between the spindle 24 and the spindle nut 26.

[0026] The spindle nut 26 is rotatably supported in the cylinder bore 20 by a bearing 28. The bearing 28 is, for example, a rolling bearing and is received in a bearing seat of a bearing shield 30, which is fixed at its circumferential surface in the cylinder bore 20 of the housing block 12. The bearing shield 30 has a central cavity in which a drive 32 is arranged, which is supported on the inner ring of the rolling bearing and is connected to the spindle nut 26 so as not to rotate relative to the spindle nut 26. The drive 32 protrudes from the hydraulic module 10 to the left as viewed in FIG. 1 and is used, for example, to transmit the rotation of a motor / transmission unit (not shown) to the spindle nut 26.

[0027] The piston 18 is fitted with two opposing support elements 34 at its open end. The support elements 34 project radially outwardly from the piston 18 in the form of wings and engage in assigned guide grooves 36 on the housing block side. The guide grooves 36 run into the housing block 12 in the direction of the longitudinal axis L of the cylinder bore 20. The support elements 34 are supported circumferentially on the sides of the guide grooves 36, so that the piston 18 and the spindle 24 connected to it cannot follow the rotational movement of the spindle nut 26. As a result, the rotational movement of the spindle nut 26 is converted into an axial movement of the piston 18 by the spindle drive or transmission 16 described. Depending on the direction of rotation, the piston 18 is driven either in the pressure-increasing direction or in the pressure-reducing direction opposite to the pressure-increasing direction. In the pressure increase direction, the piston (18) enters the working chamber (22) and displaces the pressure medium contained therein into the connected brake circuit (not visible). When the piston (18) moves in the opposite direction, i.e. in the pressure reduction direction, the volume of the working chamber (22) increases, pressure medium flows back into this working chamber (22) from the brake circuit and the pressure level in the connected brake circuit correspondingly decreases.

[0028] As explained, the piston 18 is guided directly in the housing block 12. Between the periphery of the piston 18 and the wall of the bore 20, there exists for this purpose a surrounding guide gap 38 which is sealed against the working chamber 22 in order to allow a pressure change in the working chamber 22 by the explained axial movement of the piston 18. The measures according to the invention taken for guiding the piston 18 in the bore 20 and sealing the guide gap 38 between the piston 18 and the bore 20 are shown in the essential part X and are explained below with the aid of the detailed description of FIG. 2, which shows this essential part X on an enlarged scale.

[0029] The mentioned guide gap (38) is sealed against the working chamber (22) by two seal assemblies (40a; 40b) in this embodiment. Both seal assemblies (40a; 40b) are respectively accommodated in assigned ring grooves (42a, 42b) which are formed at an axial distance from one another in the inner wall of the cylinder bore (20). The first seal assembly (40a) or high-pressure seal on the working chamber (20) side is configured as a multi-chamber seal ring, the individual chambers of which open towards the working chamber (22). The pressure medium from this working chamber (22) under pressure can thus flow into said chambers and press or press the seal assembly (40a) against the side of the surrounding ring groove (42a) or against the piston circumference.

[0030] The second seal assembly (40b) is arranged on the opposite side of the first seal assembly (40a) from the working chamber (22) and is configured as a lip seal ring having two seal lips. The first seal lip abuts against the bottom of the ring groove (42b), and the second seal lip abuts against the piston peripheral surface. The second seal assembly (40b) is axially supported by the closed side of the second seal assembly (40b) on the side of the ring groove (42b) that is remote from the working chamber.

[0031] Between the two ring grooves 42a, 42b for the seal assembly 40a, b, a similarly ring-shaped receiving groove 44, which receives a guide element 46 for the piston 18, is arranged in the wall of the cylinder bore 20. In the radial direction of the groove 44, i.e. starting from the side of the groove 44 that opens towards the piston 18, the groove 44 is stepped inwardly once at a right angle in cross section, so that it is divided into two transitional groove sections of different axial extent or width. The transition between the groove sections forms an abutment shoulder 48 against which the guide element 46 received in the wider groove section of the groove 44 is supported on the edge side, while the central area of ​​the guide element 46 overlaps the narrower groove section of the groove 44.

[0032] The guide element 46, which by way of example has a rectangular cross section, projects radially from the receiving groove 44 in a section into the guide gap 38 between the piston 18 and the cylinder bore 20. The groove section of the receiving groove 44 in which the guide element 46 resides is made wider, as viewed in the direction of the longitudinal axis L of the hydraulic module 10, than the section of the guide element 46 which projects into this receiving groove 44, so that the guide element 46 is received in the receiving groove 44 with lateral and / or axial play in both spatial directions.

[0033] The narrower groove sections of the receiving grooves 44 are located on the side of the shoulders 48 facing away from the piston 18 and extend radially between these shoulders 48 and the bottom of the receiving grooves 44. These groove sections communicate with cavities, not visible in the drawings, provided in the housing block 12, in which pressure medium at atmospheric pressure is present. These cavities, e.g. channels or chambers, are preferably connected to a pressure medium reservoir. The pressure medium at atmospheric pressure thus reaches the rear surface of the guide element 46 facing away from the piston 18 through the narrower groove sections of the receiving grooves 44.

[0034] The guide element (46) is manufactured from a material with good sliding properties that is resistant to brake fluid, for example from PTFE. The guide element (46) is formed as a ring with a slit, the free ends of which are located opposite each other. The slits S through the guide element (46) run obliquely to the longitudinal axis L. The end faces of the free ends of the slits S are radially chamfered, i.e. from the outside to the inside, in each case in the same direction, so that even with a slight radial pressure against the circumference of the guide element (46), the two ends ride up against each other and slide apart, so that the outer diameter of the guide element (46) is reduced and at the same time its radial preload is increased. Conversely, the slits S across the guide element (46) likewise allow the radial expansion of the guide element (46). Radial expansion of the guide element 46 is permitted, for example, if the piston 18 resting against the guide element 46 acts on its inner circumference with a radial force during operation of the piston 18 due to the manufacturing tolerances of the components of the transmission 16. In the installed state, the maximum possible expansion of the guide element 46 is, as mentioned, limited by the abutment shoulder 48 of the receiving groove 44, so that the guide element 46 is effectively protected against overload or damage.

[0035] In order to prevent the piston (18) from coming into contact with the wall of the cylinder bore (20) of the housing block (12), the dimensions of the guide element (46) and the position of the abutment shoulders (48) of the receiving groove (44) are coordinated with one another in such a way that, when the guide element (46) abuts against these abutment shoulders (48) with its back surface facing away from the piston, the guide element (46) radially projects in a section into the guide gap (38) between the piston (18) and the wall of the cylinder bore (20).

[0036] Through the slits S, the pressure medium flows into the inside of the guide ring (46) on the side of the piston (18). In addition, the pressure medium flows along the outside or side of the guide element (46) to the piston circumference and from there spreads towards both seal assemblies (40a, b). The sealing lips of these seal assemblies (40a, b) resting against the piston circumference and the guide ring (46) are lubricated in this way, cause only a small frictional resistance against the piston (18) and are subject to at most only a small amount of wear.

[0037] The sealing groove (42a) divides the bore (20) into a bore section facing the working chamber (22) and a bore section facing away from the working chamber (22). The bore section facing the working chamber of the bore (20) may be configured with a slightly larger inside diameter than the bore section facing away from the working chamber, so that the guide gap (38) between the piston (18) and the wall of the bore (20) is slightly larger on the working chamber side, allowing the piston (18) to assume a certain tilted position relative to the longitudinal axis L during operation of the piston (18) without the piston periphery coming into contact with the wall of the bore (20). The maximum tilted position of the piston (18) and thus the enlargement of the inside diameter of the bore (20) in the bore section facing the working chamber is determined by the structural design of the guide ring (46) and the assigned receiving groove (44).

[0038] Figures 3 and 4 show the assembly process of the guide element. For this purpose, Figure 3 shows in a three-dimensional exploded view the already described housing block (12), in which a cylinder bore (20) for the piston (18) of the piston pressure generator (14) is formed, an assembly sleeve (50) with a single offset in its outer diameter, which is ready to be introduced into said cylinder bore (20), and finally a guide element (46) with a cut-through slit S, which is to be placed by means of said assembly sleeve (50) in the receiving groove (44) formed in the inner circumferential surface of the cylinder bore (20). The guide element (46) is shown in a relaxed state, with both free ends of the guide element (46) lying opposite each other at a distance from each other, and the slit S, which is oriented obliquely with respect to the longitudinal axis L, being thereby open.

[0039] 4 shows an enlarged longitudinal section of a housing block 12 with a cylinder bore 20. The cylinder bore 20 passes through the housing block 12 from a first flat or upper surface 52 of the housing block 12 to a second flat or lower surface 54 located parallel to the housing block 12. After the cylinder bore 20 is manufactured, a total of three ring-shaped grooves 42a, 42b, 44 are formed along the inner wall of the cylinder bore 20 by means of a suitable tool. The three grooves 42a, 42b, 44 are arranged at intervals from one another in the region of the cylinder bore 20 close to the lower surface, as viewed in the direction of the longitudinal axis L of the cylinder bore 20. The outer grooves (42a, 42b) are of rectangular cross section with continuous lateral sides and are provided to receive the seal assemblies (40a, 40b) disclosed in connection with the description of FIG.

[0040] The third ring groove or receiving groove (44), which is arranged between the two outer ring grooves (42a, 42b), is radially recessed into the housing block (12) shallower than the two outer ring grooves (42a, 42b). In cross section, the third ring groove or receiving groove (44) is offset once at right angles radially outwardly starting from the inner wall of the bore (20) and is therefore divided, as viewed in the direction of the longitudinal axis of the bore, into a first groove section which is wider and a second groove section which is narrower than the first groove section and forms the groove bottom. The two groove sections merge into one another, the transition being configured as described at right angles, so that a concentric abutment shoulder (48) is formed against the inner wall of the bore (20) (FIG. 2).

[0041] An assembly sleeve 50 is inserted into the cylinder bore 20 thus prepared. The assembly sleeve 50 is made of, for example, a plastic material and has at one end a radially extending flange 50a, with which the assembly sleeve 50 rests flush against the upper surface 52 of the housing block 12. A shaft 50b of the assembly sleeve 50, which is connected to the flange 50a, extends into the cylinder bore 20 and rests flush against the wall of the cylinder bore 20. The extension of the shaft 50b is dimensioned in such a way that in the installed state, the assembly sleeve 50, as viewed in the lead-in direction, ends after the first ring groove 42b for the first seal assembly 40b, just before the receiving groove 44 for the guide element 46.

[0042] The assembly sleeve (50) is formed in the flange region with a lead-in bevel (50c) whose inside diameter decreases continuously from the outside to the inside of the assembly sleeve (50). At its opening to the periphery, the lead-in bevel (50c) has an inside diameter slightly larger than the outside diameter of the guide element (46) without radial preload. In this preload-free state, the free ends of the guide element are located opposite each other with a small distance between them and the slit S through the guide element (46) is open.

[0043] Now, when a force directed in the direction of the longitudinal axis L of the cylinder bore 20 is applied from the outside to this guide element 46 by a punch or the like, this guide element 46 slides along the lead-in bevel and the mentioned slit S starts to close. Since the end faces of the ends of the guide elements 46 are radially chamfered in the same direction, as soon as they come into contact with each other, they slide over each other, so that the outer dimension of the guide element 46 gradually decreases until it becomes equal to the inner diameter of the assembly sleeve 50 in the region of its shaft 50b. At the same time, a radial preload is applied to the guide element 46.

[0044] The guide element 46, which is thus preloaded, is advanced further along the shaft 50b into the bore 20 and finally beyond the opposite end of the shaft 50b. When the guide element 46 is completely out of the assembly sleeve 50, the preload is relaxed and the guide element 46 snaps into the receiving groove 44 provided in the wall of the bore 20 directly where the shaft 50b of the assembly sleeve 50 terminates.

[0045] Due to the remaining radial preload, the guide element (46) rests on its circumferential surface against the abutment shoulder (48) of the receiving groove (44) and, in some sections, projects beyond the opening of the receiving groove (44) into the interior of the cylinder bore (20), as shown in FIG. 2.

[0046] The punch and assembly sleeve (50) are now no longer needed and may be removed from the housing block (12) or cylinder bore (20).

[0047] The piston 18 is then introduced into the bore 20, starting from the piston head of the piston 18. The transition from the piston head to the piston skirt is provided with a radius or phase, so that the piston 18 slightly expands the guide element 46 as soon as the piston 18 engages with it, thus applying an additional preload to the guide element 46. In the assembled position, the guide element 46 is fixedly arranged in the receiving groove 44. The guide element 46 then surrounds the circumference of the piston 18 and radially supports it in the bore 20 when the piston 18 is driven by the transmission 16 to reciprocate in the bore 20.

[0048] It is obvious that modifications or additions can be made in the described embodiment without departing from the scope of the rights defined by the appended claims. [Explanation of symbols]

[0049] 10 Hydraulic Module 12 Housing Block 14 Piston pressure generator 16 Transmission Mechanism 18 Piston 20 Cylinder hole 22 Working chamber 24 Spindle 26 Spindle nut 28 Bearings 30 Bearing Shield 32 Drive unit 34 Supporting elements 36 Guide groove 38 Guide gap 40a Seal Assembly 40b Seal Assembly 42a Ring groove, seal groove 42b Ring groove 44 Receiving groove, ring groove 46 Guide elements, guide rings 48 Contact shoulder 50 Assembly Sleeve 50a flange 50b shaft 50c Introduction Slope 52 First flat surface or top surface 54 Second flat surface or bottom surface A double arrow, axial movement L Longitudinal axis S slit X main part

Claims

1. A hydraulic module (10), in particular a hydraulic module (10) for generating and / or regulating brake pressure in a slip-controllable vehicle brake system, comprising: a housing block (12) in which a cylinder bore (20) is formed; a piston (18) of a piston pressure generator (14) received within the cylinder bore (20) and defining a working chamber (22); a transmission mechanism (16) capable of driving the piston (18) for an axial movement A in a pressure increase direction or in a pressure reduction direction opposite to the pressure increase direction; Equipped with the volume of the working chamber (22) decreases when the piston (18) moves in a pressure increasing direction, or increases when the piston (18) is driven in a pressure decreasing direction; and a surrounding guide gap (38) is provided between the peripheral surface of the piston (18) and the wall of the cylinder bore (20), and the guide gap (38) is sealed toward the working chamber (22) by a seal assembly (40a); In the hydraulic module (10), a guide element (46) is provided on the seal assembly (40a) on a side facing away from the working chamber (22), by means of which the piston (18) can be supported radially in the cylinder bore (20) at its circumferential surface; the guide element (46) is accommodated in an accommodation groove (44) provided in the wall surface of the cylinder bore (20) such that the guide element (46) projects radially into the guide gap (38) at a portion of the guide element (46); 1. A hydraulic module, in particular for generating and / or regulating brake pressure in a slip-controllable vehicle brake system, comprising:

2. 2. A hydraulic module according to claim 1, characterized in that the guide element (46) is a shape-resilient ring element, which is slotted and has two free ends situated opposite each other.

3. 3. Hydraulic module according to claim 1 or 2, characterized in that the guide elements consist of PTFE or a plastic resistant to brake fluids.

4. 4. The hydraulic unit according to claim 1, wherein the receiving groove (44) of the guide element (46) is arranged between a first seal assembly (40a) directly facing the working chamber (22) and a second seal assembly (40b) remote from the working chamber (22).

5. 5. The hydraulic module according to claim 1, wherein the receiving groove (44) is stepped from the outside to the inside, as viewed in cross section of the receiving groove (44), and forms an inner abutment shoulder (48) on which the guide element (46) can be supported radially.

6. 6. The hydraulic module according to claim 5, characterized in that the groove section of the receiving groove (44) formed between the abutment shoulder (48) and the groove bottom is in communication with a pressure medium conducting cavity provided in the housing block (12).

7. 7. Hydraulic module according to claim 1, characterized in that the guide element (46) is received in the receiving groove (44) with axial play.

8. 8. An assembly method for a hydraulic module according to any one of claims 1 to 7, comprising the steps of: A housing block (12) is provided with a cylinder bore (20) and an accommodating groove (44) for a guide element (46) therein; An assembly sleeve (50) is inserted into the cylinder bore (20); Introducing a guide element (46) into said assembly sleeve (50); and applying a forward driving force directed in the longitudinal direction L of the bore (20) to the guide element (46) until it comes out of the assembly sleeve (50) at the opposite end and snaps into the assigned receiving groove (44), 13. An assembly method for a hydraulic module, comprising:

Images