Pressure device with support element

Abstract

For pressure devices (10, 184), particularly for hydraulic assemblies (12) of vehicle braking systems, there is a piston (22) that can be axially guided in a cylinder (40) and a motor (14, 186) that can selectively move the piston (22) axially in two directions. The cylinder (40) is designed to have a receiving portion (20) arranged in a hydraulic housing (18) with a receiving opening (28) at its end (26) facing the motor (14, 186). The receiving opening is partially covered by a support element (72), wherein a component (73) coupled to the motor (14, 186) is supported at the hydraulic housing (18) by the support element (72), and the support element (72) is held at the hydraulic housing (18) by a push-in fit (97) to withstand radial and axial forces generated during operation.

Description

Technical Field

[0001] This invention relates to a pressure device, particularly a pressure device for a hydraulic assembly of a vehicle braking system, the pressure device having a piston axially guided in a cylinder and a motor selectively axially moving the piston in two directions, wherein the cylinder is designed to have a receiving portion arranged in a hydraulic housing, the receiving portion having a receiving opening at its motor-facing end, the receiving opening being partially covered by a support element, wherein a component coupled to the motor is supported at the hydraulic housing by means of the support element, and the support element is held at the hydraulic housing. Background Technology

[0002] Known vehicle braking systems are used in motor vehicles, such as passenger cars or trucks, to provide regulated braking pressure to associated wheel brakes, thereby achieving, for example, anti-skid adjustment. The core component of such adjustable braking systems is a hydraulic assembly with hydraulic structural elements, typically connected to the master brake cylinder. The driver issues a braking request via a pedal, at which point a controller adjusts the braking pressure to be generated by an electric motor. Here, a pressure device, more precisely an external force pressure device, operated by an electric motor, serves as an external force source to generate braking pressure. This pressure device is typically designed as a piston-cylinder unit, having a piston that is movably guided within the cylinder and an actuator that selectively moves the piston, driven by an electric motor. The resulting braking pressure is transmitted to the wheel brakes via hydraulic or electromechanical actuators. Under normal braking conditions, the master brake cylinder is decoupled from the wheel brakes and is used to detect the driver's braking request.

[0003] Depending on the vehicle type and size, different types of braking systems are required. These systems have different power outputs, structural forms, and operating modes, and contain related structural components that differ in parts or size. Pressure devices that should be operated by electric motors must also be designed accordingly. Furthermore, new vehicle developments are leading to increasing levels of driving automation, which places new demands on braking systems. In particular, the pressure generation using external force sources must be exceptionally reliable and safe to operate, eliminating the need for driver intervention. Summary of the Invention

[0004] The object of the present invention is to provide a pressure device that achieves a particularly compact and safe structure for pressure generation, and which can also be manufactured as cost-effectively as possible.

[0005] According to the invention, a pressure device or hydraulic module, particularly an external pressure device, is proposed, especially for hydraulic assemblies of vehicle braking systems, and has a piston that can be axially guided in a cylinder and a motor that selectively moves the piston in two directions, the motor being an actuator. The cylinder is designed to have a receiving portion arranged in a hydraulic housing or housing, the receiving portion having a receiving opening at its motor-facing end, the receiving opening being partially covered by a support element. The component coupled to the motor is particularly an actuator, and preferably a support for the actuator element, supported at the housing by the support element, and the support element is held at the housing. Here, the support element is coupled particularly directly to the housing by means of a push-in fit (Schiebesitz) to withstand radial and axial forces generated during operation. By means of this push-in fit, the support element is particularly adapted to counteract or offset radial forces. To produce the push-in fit, the support element can be pushed against the housing, particularly surrounding the receiving opening. The support element partially covers the receiving opening, particularly by providing an axial opening in the support element. Therefore, the support element is preferably designed in a cup shape with a cup bottom, and the opening is arranged in the cup bottom.

[0006] By means of this force-transmitting coupling of the support element at the housing according to the invention, a particularly wide range of support is achieved for the radial and lateral moments acting relative to the axis of the associated housing generated during the operation of the pressure device. Lateral refers to perpendicular to and inclined to the axis of the housing. This achieves particularly stable and durable fixation of the support element at the housing. Particularly advantageously, for the push-in fit, there is radially inner contact between the support element and the housing, and radially outer contact with the material surrounding the support element of the housing. This allows the support element to be supported by the housing on both radial sides. This achieves a particularly wide range of force transmission from the force acting on the support element during operation to the housing. Here, the radially outer contact is preferably achieved by a flanged connection with the housing, which deforms the material surrounding the support element.

[0007] Support elements are used to support components coupled to the motor's power transmission, particularly actuators. Here, the component is specifically a support for the actuator element, while the support element functions as a support retainer or cover. Preferably, the actuator element is a nut that fits into the spindle thread of the main shaft, and this nut can be rotated by a motor or electric motor belonging to the actuator. For this purpose, the nut is rotatably supported, particularly in the axial region at its end, by a rotary support acting as a support. Thus, the support for the component is correspondingly coupled to the motor's power transmission. When the nut rotates, its rotational motion is converted into the axial motion of the main shaft via the spindle thread. At this time, the main shaft moves the piston coupled with it axially into the receiving portion along the pressure direction, or the pressure-increasing direction. Here, pressure is applied to the pressure medium located in the receiving portion and the associated working chamber, thereby expelling the pressure medium from the working chamber. The resulting reaction force is correspondingly transmitted to the housing through the support and support elements. In this case, the push-fit according to the invention allows the force to be dissipated to the housing over a particularly large range in the radial, oblique, and axial directions. Furthermore, by reversing the rotational direction of the motor, the main shaft and therefore the piston move axially in the opposite direction toward the support element, or in other words, in the direction of pressure reduction. This reversal of rotational direction can be achieved, in particular, by using different motor windings. The resulting force is correspondingly transmitted to the housing. Specifically, the housing is designed as a hydraulic block, through which the correspondingly stable torque is absorbed. This forms a pressure device integrated into the housing, or rather, a torque-transmitting hydraulic module integrated into the housing.

[0008] Advantageously, the pressure device is designed with a cup-shaped piston movable within a housing, in which a main shaft fixedly connected to the piston (i.e., fixed in both the axial and rotational directions) and a nut rotatable around the main shaft by a motor are arranged. Preferably, more than half the length of the nut is enclosed by the piston. Additionally, a support element is provided, coupled to the housing via a push-fit connection. This support element serves as a support housing to support the generated axial force and ensure the concentricity of the rotating nut and the axially moving main shaft. Preferably, the support element is directly coupled to the housing or held within the housing. Particularly noteworthy is that the cylinder block is formed directly from the housing housing, rather than a cylinder liner conventionally housed within the housing. This also achieves direct support of the generated torque at the housing.

[0009] Advantageously, according to the invention, the push-in fit is designed as an interference fit. For this purpose, the support element is preferably designed as a cup shape, and in its unassembled state, its diameter in its support section is equal to or slightly smaller than the diameter of the material surrounding the receiving opening of the housing, onto which the support element is then pushed under pressure and thus press-fitted. This forms an interference fit as a force-transmitting connection, which dissipates radial and lateral forces generated during operation particularly well.

[0010] Furthermore, according to the invention, the push-in fit is advantageously designed as a form fit, allowing for particularly simple assembly. For such a form fit, the support element preferably has at least one hook or tooth on its side facing the housing, which engages with the housing in a form fit manner. For this purpose, it is particularly preferred to provide multiple hooks or teeth, and especially preferably to form a toothed bend between the support element and the material of the housing surrounding the receiving opening.

[0011] Furthermore, according to the invention, the support element is advantageously axially abutted against the hydraulic housing via a contact surface. Here, the contact surface extends transversely to the axis of the receiving portion. Preferably, the contact surface extends obliquely, and particularly preferably perpendicular to the axis of the receiving portion. Thus, the support element is axially supported at the housing, absorbing the corresponding axial forces, particularly the forces from the translational movement of the piston, and transmitting these forces axially to the housing. Furthermore, the maximum stroke or stroke space of the piston is determined by the contact surface or its corresponding axial position. Therefore, the pressure device is characterized radially by the circular cross-section of the receiving portion, and axially primarily by the contact surface against which the support element abuts. Here, the support element is axially abutted against the housing via the contact surface in such a way that the support element has a radially extending flange that abuts against the contact surface and is preferably axially upset with the housing material on its radially outer side. Particularly preferably, this flange is axially upset with the housing material over the entire circumference. Alternatively, the support element is held at the housing on its radially outer side by a clamping portion surrounding the flange of the support element. By using axial contact, especially upsetting or fixing via clamping, the axial orientation of the pressure device relative to the sun gear associated with the motor is determined and maintained.

[0012] Advantageously, within the housing, a groove extending around the receiving opening is arranged on the housing side facing the motor, and the support element is designed in a cup shape with a flange extending radially outward, wherein the flange is received in the groove, such that the support element abuts against the groove surface radially inward by a push-fit, and / or the flange is upset to the housing material surrounding the groove radially outward by an upsetting. Here, the support element abuts against the bottom of the groove with its flange, which serves as the axial contact surface of the support element. Thus, in addition to forming a particularly stable coupling between the support element and the housing, a particularly compact force transmission coupling is also formed. In particular, the support element extends beyond the receiving portion in the direction away from the motor and extends into the housing through the groove. Therefore, the axial region of the push-fit between the support element and the housing simultaneously serves as a stroke space within the receiving portion, parallel to the axial region. This configuration provides ample mounting space for the cylinder of the pressure device, while the cylinder is arranged in a space-saving manner along the direction of the receiving portion and its axis. In this case, the axis of the receiving portion determines the Y direction of the housing. Therefore, it also saves installation space along the Y direction.

[0013] Advantageously, the groove is designed here with a small step on the radially outer side, against which the forming tool can be abutted to upset the housing and the support element together. This guides the forming tool at the radially outer axial edge region left on the radially outer groove surface and facilitates upsetting with the aid of the step.

[0014] Furthermore, according to the invention, the receiving portion advantageously has at least one axial anti-rotation groove to correspondingly accommodate a guide portion extending radially from the piston. Here, the push-in fit is interrupted, particularly in the region of the at least one axial anti-rotation groove. Surprisingly, despite the interruption of the push-in fit, the support element remains stably held in the housing. This achieves a space-saving design, where each anti-rotation groove is used to correspondingly accommodate the guide portion extending radially from the piston, thereby preventing undesirable rotation of the piston during its axial movement. Additionally, each axial anti-rotation groove preferably opens to a receiving opening located at the end facing the motor. Here, the support element, in particular, surrounds each axial anti-rotation groove with its cup wall, such that the radial contact area formed by the push-in fit is interrupted in the region of the anti-rotation groove and extends axially parallel outside the receiving portion beyond the region of the anti-rotation groove. Thus, the support element, in particular, partially overlaps the receiving portion in the axial direction with its cup wall. This overlapping area, axially parallel, serves as a space-saving stroke space within the receiving portion. Furthermore, at least one anti-rotation groove or longitudinal groove has an axial dimension by which the stroke space is limited on its side away from the motor. Therefore, a compact arrangement of the support element and the receiving portion is achieved in the Y direction, wherein at least one axial anti-rotation groove is preferably compactly surrounded by the support element in both the radial and X and Z directions.

[0015] The receiving portion has an associated radial bulge in its cross-section, defined by at least one axial anti-rotation groove, which determines the maximum outer diameter of the receiving portion in its cross-section. Preferably, the inner diameter of the push-fit in its cross-section is equal to the maximum outer diameter, such that the push-fit is interrupted in the region of each anti-rotation groove. Alternatively and preferably, the inner diameter of the push-fit is smaller than the maximum outer diameter. Thus, the at least one axial anti-rotation groove extends radially beyond the push-fit and provides additional space there to accommodate the associated guide portion, particularly extending radially from the piston, during insertion. In an alternative preferred improvement, the inner diameter of the push-fit is larger than the maximum outer diameter, thereby allowing the push-fit to extend particularly stably throughout the circumferential direction at the housing. This design is advantageous when there is sufficient space for this in and at the housing.

[0016] Advantageously, according to the invention, the receiving portion has a receiving portion axis extending perpendicularly to two opposing housing sides of the housing and located in a first imaginary plane, which extends parallel to the memory side of the housing adjacent to the two housing sides. Here, at least one axial anti-rotation groove extends parallel to the receiving portion axis with its groove axis or groove center axis, wherein the groove center axis and the receiving portion axis are located in a second imaginary plane such that the second imaginary plane is rotated about the receiving portion axis by an angle of 10° to 50°, preferably 20° to 40°, and particularly preferably 30° about the first imaginary plane. Specifically, this angle is oriented counterclockwise when the viewing angle is towards the housing side serving as the motor side. Therefore, further optimization of the mounting space is achieved in the X and Z directions, at the motor side, by which collisions with other structural elements are avoided. Preferably, two axial anti-rotation grooves arranged according to the aforementioned angle and diametrically opposed about the receiving portion axis are provided. Therefore, during the optimization of the mounting space, a particularly uniform supporting force is simultaneously applied to the housing in the X and Z directions to prevent piston rotation.

[0017] Furthermore, according to the invention, the support element is advantageously surrounded by the motor housing of the motor, which is fixed to the housing by two fixing points that are diametrically opposed to each other, particularly on the housing side or motor side facing the motor. The space-saving fixing of the motor housing and thus the motor on the motor side is achieved with only two fixing points, which, combined with a radially force-bearing push-in fit of the support element, remains sufficiently stable. Here, the combination of an interference fit on the radially inner side and a upset fit on the radially outer side of the support element at the housing has proven particularly advantageous. This creates more space on the motor side and in the X and Z directions for further accommodation of other structural elements, enabling optimized installation space in the X and Z directions. For further optimization, the two fixing points are particularly located on an imaginary straight line that forms an angle of 10° to 50°, preferably 20° to 40°, and particularly preferably 30° with the plane of the housing side opposite the memory side. Therefore, the two fixing points are arranged in a column that extends obliquely to the housing side opposite the memory side and thus obliquely to the motor side. This angled arrangement allows the motor housing to be positioned, in a space-saving manner, particularly close to the corner of the motor side. Only sufficient space needs to be provided for a flange radially surrounding the motor housing, which rests against the motor side. Preferably, a seal is provided between the flange and the motor side to prevent moisture from seeping into the motor housing. Specifically, the motor housing is cup-shaped with a radial flange having two lugs opposite each other along its diameter, each lug being threaded onto the motor side.

[0018] Advantageously, according to the invention, the receiving portion has another receiving opening at its end opposite to the motor, which is closed by a cup-shaped cylinder head. Specifically, the receiving portion has a radial sealing groove between the axial anti-rotation groove and the other receiving opening, in which a piston seal surrounding the piston is received, thereby preferably ensuring that the working chamber enclosed by the receiving portion, the cup-shaped cylinder head, the piston seal, and the piston has no passageway to a memory unit that can be arranged in the housing. By eliminating the passageway to the memory unit, particularly in the piston's rest position or zero position, more efficient use of the stroke space is achieved, and thus further reduction in the installation space in the Y direction. There is no dead stroke, and the associated cylinder volume can be fully utilized; the total volume is essentially equal to the net volume. Preferably, pressure balance in the rest position is achieved at this time by a control valve connected to the working chamber, which is designed as a normally closed solenoid valve, especially a normally closed solenoid valve with hydraulic relief function.

[0019] Particularly advantageously, in the receiving section, an additional radial sealing groove is provided axially between the axial anti-rotation groove and the radial sealing groove, and a radial guide groove is arranged axially between the two sealing grooves, which is connected to a pressure medium, particularly at atmospheric pressure. The guide groove is preferably arranged concentrically with the two sealing grooves and serves to connect the pressureless area to the pressure medium, which preferably originates from other pressureless cavities within the storage unit or housing, particularly at atmospheric pressure. Preferably, the guide groove is connected to the storage unit for this purpose, specifically such that the region of the guide groove opposite to the piston is radially or obliquely cut, but not penetrated, by the conduit connecting to the guide groove. This achieves pressureless balance of the pressure medium in the region between the two sealing grooves. The piston seal serving as a high-pressure seal is housed in the sealing groove facing the working chamber, while the piston seal serving as an isolation seal in that low-pressure region is housed in the sealing groove opposite to the working chamber. The guide groove ensures that both piston seals are wetted on the back pressure side during operation. This lubricates the piston seals that are in contact with the piston's periphery, reducing wear and frictional resistance at the piston. Furthermore, the guide groove preferably accommodates an annular guide portion that extends slightly radially beyond the accommodating portion, allowing the piston to be guided with a gap between it and the accommodating portion.

[0020] Furthermore, according to the invention, it is advantageous that the working chamber is fluidly connected to a corresponding control valve of the associated braking circuit via at least one axial inflow and outflow portion. Preferably, on the housing side serving as the controller side, the at least one inflow and outflow portion has a conduit opening located radially outward near the receiving opening. Specifically, axial conduit sections are guided from each conduit opening into the housing, leading to a conduit section preferably extending transversely to the axis of the receiving portion, which connects to the associated control valve. Preferably, a radially surrounding groove is arranged on the controller side, in which the conduit openings are arranged. Additionally, a housing shoulder is formed between the groove and the receiving opening, and the cylinder head is press-fitted to this housing shoulder at its inner cup wall. The resulting radially inward interference fit is partially interrupted by the corresponding inflow and outflow portions. Here, the cylinder head particularly has a radially outwardly extending flange that is upset to the housing material on the radially outward side and thus reliably held in the housing. Accordingly, when the piston moves toward the cylinder head or into the working chamber, the pressure medium can be axially expelled from the working chamber through the pipe opening, or when the piston moves out, the pressure medium can be axially drawn into the working chamber through the pipe opening. This allows for a particularly compact inflow and outflow of the pressure medium.

[0021] Furthermore, the pressure medium is advantageously drawn from the reservoir into the working chamber through a recess at at least one of the axial inflow and outflow portions, which increases the cross-section of the inflow and outflow portions. This recess is preferably designed to be kidney-shaped, and the interference fit is interrupted by the recess to a greater extent than by the interruption caused solely by the pipe opening. This results in a simple and effective back pressure reduction in a so-called single-cassette braking system for compensating filling or supplemental intake, in which the braking pressure actuation and modulation unit is housed in a single housing.

[0022] Furthermore, according to the invention, the support element is a protruding element adapted to be identical in its protrusion relative to the housing for various pressure device types, while the receiving portion is adapted to have different axial dimensions for various types of pressure devices. Here, the protrusion is defined by an axial extension and a radial extension away from the housing. Specifically, for various pressure device types, the protrusion is designed to have at least the same axial extension. Preferably, for various pressure device types, the protrusion is also designed to have the same radial extension. Particularly preferably, the support element and / or the protruding element are designed to be structurally identical, thereby achieving a cost-effective economies of scale. Here, the support element is preferably surrounded by a cover element in which other transmission components are arranged. Here, for various pressure device types, except for the support element, the cover element is preferably identical in its protrusion relative to the housing. Here, the support element and the cover element together constitute the protruding element, which is designed to be identical in its protrusion and structure for various pressure device types.

[0023] In other words, according to the invention, it is advantageous to provide a series of pressure devices having at least two types of pressure devices, each type of pressure device being designed with a protruding element belonging to a support element and a receiving portion. Here, the protruding elements belonging to the support element in the at least two types of pressure devices are designed to be structurally identical, while the receiving portions in the at least two types of pressure devices are designed differently with respect to their axial dimensions.

[0024] This design allows such pressure devices to be adapted to different types of associated vehicle braking systems in a simple, cost-effective, and particularly easy-to-assemble manner. The axial dimension of the housing according to the invention can be easily changed. In particular, this can be achieved by altering the housing thickness of the associated housing. Here, the housing thickness extends between the motor side and the opposite controller side of the housing, where the electronic controller controlling the motor is arranged, and the housing extends axially from the motor side to the controller side. Thus, by simply changing the housing thickness, different variations in the length of the housing can be obtained, resulting in different variations in the cylinder length. Different cylinder lengths cause different volumes of the pressure device and correspondingly different power outputs. Therefore, only minor adjustments to the housing are needed, and if necessary, only adjustments to a very small number of other components. The design of the support elements, preferably the protruding elements, and preferably other components is identical. This results in increased production volume and advantageous economies of scale.

[0025] Advantageously, according to the invention, the receiving portion has at least one axial anti-rotation groove to accommodate a guide portion extending radially from the piston, wherein the at least one anti-rotation groove is designed to have different axial dimensions for various pressure device types. This achieves simple adaptation to receiving portions having correspondingly different axial dimensions.

[0026] Advantageously, according to the invention, a very simple adaptation is thus achieved: the receiving portion has at least one radial sealing groove to accommodate the piston seal accordingly, wherein, for various pressure device types, the at least one sealing groove is arranged in the receiving portion at correspondingly associated different axial positions.

[0027] Furthermore, according to the invention, the protruding element, which is a support element, is surrounded by the motor housing of the motor, which is adapted to have different axial dimensions depending on the motor class or power for various pressure device types. This enables a modular design of the housing of the actuator's transmission device within the motor housing, wherein the same protrusion exists for different housing lengths or cylinder lengths and in different braking systems. Moreover, the identical protrusion of the support element or protruding element provides a unified motor interface for various pressure device types. Different motor classes can be easily interchanged within a braking system, which is cost-effective, and the transmission devices accordingly have the same protrusion. This achieves motor interchangeability and compatibility.

[0028] Furthermore, according to the invention, the receiving portion has another receiving opening at its end opposite the motor, which is closed by a cup-shaped cylinder head. Here, the cylinder head is adapted to be structurally identical for various pressure device types. Therefore, regardless of the type of pressure device used, the corresponding associated controller is always covered with the same cylinder head on the controller side, so as not to affect the controller's circuit board. Different stroke space capacities are achieved solely based on different axial dimensions of the receiving portion and thus on different housing thicknesses. Here, the receiving portion extends from the motor side to the controller side and penetrates the housing thickness of the corresponding associated housing type.

[0029] In summary, this results in a pressure device as an integrated hydraulic module for converting electrical energy into hydraulic work, featuring stable axial fixation while achieving space-optimized torque support on the housing side. Furthermore, it enables modular expansion for different braking systems, volumes, and motor sizes. Therefore, the necessary adaptations and requirements for different pressure device types can be flexibly met, while remaining cost-effective in terms of manufacturing technology. Accordingly, the invention also aims to apply this pressure device to hydraulic assemblies of various hydraulic assembly types for corresponding vehicle braking systems. This allows for the particularly space-efficient use of structurally identical components in various hydraulic assembly types, for example, for: the aforementioned single-cassette system of the so-called integrated power brake (IPB); or the actuator unit of the dual-cassette system of the decoupled power brake (DPB), wherein the brake pressure actuator and modulation unit are arranged in two different housings; or other pressure generating systems. Attached Figure Description

[0030] The embodiments of the solution according to the present invention will now be explained in more detail with reference to the accompanying drawings. Wherein:

[0031] Figure 1 A schematic longitudinal sectional view of a first embodiment of the pressure device according to the present invention is shown;

[0032] Figure 2 It shows that according to Figure 1 Details II;

[0033] Figure 3 It shows that according to Figure 1 Details III during the upsetting process;

[0034] Figure 4 A partial perspective view of the hydraulic housing in relation to the second embodiment is shown;

[0035] Figure 5 The second embodiment is shown according to Figure 1 The sectional view VV;

[0036] Figure 6 The hydraulic assembly associated with the embodiment is shown according to Figure 1 View VI;

[0037] Figure 7 A comparison of longitudinal sectional views of a third and fourth embodiment of two pressure device types according to the present invention is shown;

[0038] Figure 8 A fifth embodiment of the pressure device according to the invention is shown. Figure 3 The view;

[0039] Figure 9 The first variant of the pressure medium inflow and outflow section is shown according to... Figure 1 View IX, not showing the cylinder head; and

[0040] Figure 10 The second variant of the pressure medium inflow and outflow section is shown according to... Figure 9 The view. Detailed Implementation

[0041] Figure 1 and Figure 2 A pressure device 10 is shown for a hydraulic assembly 12 of an electro-hydraulic vehicle braking system (not shown) or a portion of the braking system shown, designed for a four-wheeled vehicle (not shown). This braking system is intended to fulfill the functions of an anti-lock braking system (ABS), electronic stability program (ESP), and / or traction control (ASR), as well as functions for at least semi-autonomous driving.

[0042] The pressure device 10 is designed as a plunger-type device, which can be driven by an electric motor or a motor 14 (only a portion of which is shown in the figure). Motor 14 is part of actuator 16 and serves as the external force actuator for the braking system, which is an externally driven vehicle braking device. Here, motor 14 and pressure device 10 function as brake pressure generators to produce braking pressure at the associated wheel brakes, constituting an external pressure source in the braking system. The braking system is currently designed as a brake-by-wire system, where the energy required for braking pressure is provided by motor 14, at least under normal braking conditions, rather than by the driver's muscle force.

[0043] Specifically, the hydraulic assembly 12 has a hydraulic housing 18, or shell 18, shown only partially, which is designed as a hydraulic block. A receiving portion 20, implemented as a stepped bore, is arranged in the housing 18; this receiving portion is a so-called external force cylinder receiving portion. A piston 22, serving as an external force piston, is received in this receiving portion; this piston is designed as a plunger or plunger-type piston. The receiving portion 20 extends axially through the housing 18 entirely along its receiving axis 24 or Y-axis, which coincides with the piston axis. Here, the receiving portion 20 is designed to open at a first end 26 facing the motor 14 or actuator 16 via a receiving opening 28. The receiving opening 28 is therefore located in the housing side 30 facing the motor 14 or actuator 16, which serves as the motor side for housing the motor 14. Furthermore, the receiving portion 20 has another receiving opening 34 at its second end 32 facing away from the motor 14 or actuator 16, which thus extends into the housing side 35, opposite to the housing side 30, which serves as the controller side.

[0044] At the housing side 35, the receiving opening 34 is sealed fluidlessly by a cup-shaped cylinder head 36 arranged coaxially with the receiving portion 20, thus elongating the receiving portion 20. Therefore, the cylinder head 36 has protruding elements 37 extending radially and axially from the housing side 35. Furthermore, the cylinder head 36 also has a radially outwardly extending flange 38, which is upset to the housing 18. The cylinder body 40 is designed as a plunger cylinder by the cylinder head 36 and the receiving portion 20, in which the piston 22 is axially movable along its axis or the receiving portion axis 24. Therefore, the cylinder body 40 is partially formed directly with the receiving portion 20 and integrated into the housing 18. A working chamber 42 is located inside the cylinder body 40 and is filled with a pressure medium, more precisely, a fluid. The working chamber 42, or pressure chamber, is sealed between the piston 22 and the housing 18 by piston seals 46 arranged in radial sealing grooves 44 within the receiving portion 20.

[0045] Here, piston seal 46 is a high-pressure seal used to seal the high-pressure area 48 defined by working chamber 42. Located opposite to working chamber 42 in another radial sealing groove 50 of receiving portion 20 is another piston seal 52 surrounding piston 22. This piston seal serves as an isolation seal to prevent leakage at the high-pressure seal and to ensure a dry area in the direction toward motor 14. A radial guide groove 53 with a T-shaped cross-section is provided axially between the two piston seals 52 and 46. Here, a conduit 54, implemented as a hole, is formed at the bottom of the guide groove 53, which is connected to the storage container 55, more specifically, the brake fluid storage container, to conduct the pressure medium. This creates a low-pressure area 56 or a pressureless area between the two piston seals 46 and 52, in which the pressure medium is at atmospheric pressure. The presence of the pressure medium here, and the connection of the conduit 54 to the guiding pressure medium in the storage container 55, ensures that the two piston seals 46 and 52 are always wetted. Furthermore, the pressure medium exists axially on both sides of the piston seal 46, thus making it a wet-to-wet type seal with particularly low wear. An annular guide portion 57 is arranged in the guide groove 53, extending slightly radially into the receiving portion 20 and circumferentially surrounding the piston 22. This guide portion guides the piston 22 and the receiving portion 20 at a corresponding interval, thereby preventing friction and jamming between the piston 22 and the receiving portion 20 (see details). Figure 2 ).

[0046] With the help of piston 22, fluid flows from working chamber 42 via Figure 9 The guide fluid inlet and outlet 58 shown is pushed into at least one brake line 59 of at least one brake circuit (not shown) to generate pressure at the associated wheel brake. Here, the working chamber 42 has no passage to the storage chamber 55. Pressure balance in the resting position of the piston 22 is preferably achieved by a control valve 60 coupled to the inlet and outlet 58. Figure 9 The control valve preferably has a hydraulic relief function (not shown).

[0047] The piston 22 is held non-rotatably and axially movable in a correspondingly associated axial anti-rotation groove 62 by means of at least one radially extending wing-shaped guide 61, with each guide 61 embedded in the respective anti-rotation groove. The anti-rotation groove 62 is formed as an elongated groove in the block housing 18 in the region of the receiving portion 20 facing the motor 14, parallel to the receiving portion axis 24. Thus, the piston 22 is supported relative to its piston axis or receiving portion axis 24 by the combined action of the guide 61 and the anti-rotation groove 62 to prevent rotation and radial movement.

[0048] Furthermore, the interior of the cup-shaped piston 22 with a circular cross-section houses a main shaft 64, which is fixedly connected to the piston 22 in both the axial and rotational directions. The main shaft 64 is surrounded by a hollow cylindrical nut 66, which engages from the outside with a form-fit thread 68 constructed on the main shaft 64. Preferably, a ball bearing (not shown) is provided between the main shaft 64 and the nut 66 as a rolling support. The nut 66 is surrounded at the end facing the motor 14 by a support 70 designed as a rotary support, which is held on the outside by a cup-shaped support element 72 fixedly coupled to the housing 18. Here, the nut 66, rotatably supported by the support 70, can be rotated by the motor 14, wherein the rotational movement causes the main shaft 64 to move via the main shaft thread 68, and thus causes the piston 22 in the cylinder 40 to move. Therefore, the support 70 is part 73 belonging to the actuator 16, and the nut 66 is the actuator element 74. Together with the motor 14 and the spindle 64, they belong to the actuator 16, which selectively moves the piston 22 within the cylinder 40. Here, the piston 22... Figure 1 The piston 22 is shown in its retracted state. If the piston 22 moves fully toward the cylinder head 36 by means of the actuator 16, the piston 22 is in the extended state. When it moves out along the pressure direction 75, the piston 22 discharges the pressure medium from the working chamber 42.

[0049] The actuator 16 also includes a transmission 76, which is preferably designed as a planetary gear transmission. For this purpose, a drive element 80 is provided, designed as a sun gear and coupled to the motor shaft 78 of the motor 14. Preferably, three planetary gears 82 engage with the drive element and are surrounded by a ring gear 83. The transmission 76, thus designed, is axially arranged outside the support element 72. For this purpose, the support element 72 has a central opening 84, coaxial with the piston 22. Axially extending elements 88 of the nut 66 are guided through the opening 84, each element correspondingly surrounded by a planetary gear 82. The opening 84 is designed with a circular cross-section and is located in the cup-shaped bottom 86 of the support element 72 facing the motor 14.

[0050] The support element 72 surrounds the support 70, which is constructed as a ball bearing, with its cup bottom 86 and associated cup wall 89. The cup wall 89 has a radially outwardly extending flange 90 axially opposite to the cup bottom 86, which is upset to the material 92 of the housing 18. Furthermore, to form the upset portion 94 radially outward, the support element 72 is also pushed radially inward around the shoulder 96 of the housing 18 with its cup wall 89, thereby forming a push-in fit 97 that withstands the radial force generated during operation. In this case, the support element 72 is press-fitted around the shoulder 96, such that the push-in fit 97 is formed by an interference fit 98 radially inward. The support element 72 thus serves as a support retainer and has a first protrusion 100 extending from or relative to the housing 18. The first protrusion 100 is defined by a first axial extension 102 and a first radial extension 104.

[0051] In the axial direction toward the motor 14, the support element 72, together with the transmission 76 and its components, is covered by a stepped cup-shaped cover element 106, which has a coaxial opening 110 in its cup bottom 108 through which the motor shaft 78 passes. The cover element 106 rests against the housing side 30 with its cup wall 112 on its open side. Thus, the cover element 106 is a transmission cover; in other embodiments not shown, this cover may rest against the support element 72 with its cup wall 112, rather than against the housing 18. The cover element 106 thus has a second protrusion 114 extending from the housing 18, the second axial extension 116 and the second radial extension 118 of which are both greater than the first protrusion 100. Therefore, the cover element 106 and the support element 72 together constitute a protruding element 120 that defines the second protrusion 114 extending from the housing 18, which is the total protrusion 114 surrounded by the cup-shaped motor housing 122.

[0052] Within the motor housing 122, a motor 14, designed as an electric motor (not shown in detail here), is axially housed behind the cover element 106 relative to the support element 72. Furthermore, the motor housing 122 has a radially extending flange 126 on its cup wall 124 opposite to the motor 14, at which two diametrically opposed lugs 128 are formed. Preferably, threaded members 130 with M5 threads are screwed into the housing 18 through these two lugs. This forms two diametrically opposed fixing points 132, which are used to secure the motor housing 122 to the housing side 30 in a very space-efficient manner (see also...). Figure 6 ) place.

[0053] Figure 3 , Figure 4 and Figure 5As shown in detail, a groove 134 is provided that extends into the block housing 18 and surrounds the receiving opening 28 in order to secure the support element 72 to the housing side 30. Thus, a so-called shoulder 96 is formed radially between the groove 134 and the receiving opening 28 in the housing 18. The shoulder 96 is formed on the outer side by the inner groove surface 136 of the groove 134, where the support element 72 is pressed against with its radially inner cup wall 89, simultaneously forming a push-in fit 97 designed as an interference fit 98. Furthermore, the groove 134 has a step 140 at its radially outer groove surface 138, on which the forming tool 142 rests to upset the housing 18 and the flange 90 together (see [reference]). Figure 3 Here, the peripheral material 92 of the housing 18 is formed on the flange 90, forming the upset portion 94.

[0054] An axial region for the push-in fit 97, or a radially abutting region 144 along the axial direction, is formed by the inner groove surface 136. This region forms an axially press-fitting region by an interference fit 98. The radially abutting region 144 extends to abutting surface 145, where the support element 72 axially abuts. Here, the abutting surface 145 extends substantially perpendicular to the axis 24 of the receiving portion and is formed by the bottom of the groove 134. Therefore, the radially abutting region 144 axially overlaps with the receiving portion 20. This overlapping region is axially parallel and serves as a space-saving travel space 146 for the piston 22's travel within the receiving portion 20 (see [link to relevant documentation]). Figure 1 Therefore, the support element 72 and the receiving portion 20 are arranged very compactly and overlapping each other along the receiving portion axis 24, or in other words, along the Y direction. In this case, the push-in fit 97 and thus the radial contact area 144 along the axial direction are interrupted by at least one anti-rotation groove 62 (see also...). Figure 1 ).

[0055] Figure 3 , Figure 4 and Figure 5 An embodiment is shown in which two axial anti-rotation grooves 62, diametrically opposed to each other, are provided as longitudinal grooves in the receiving portion 20 relative to the receiving portion axis 24. Each anti-rotation groove 62 accommodates a guide portion 61 extending radially outward from the piston 22. This design allows the push-in fit 97 to be in the assembled state (see...). Figure 5The anti-rotation groove 62 is interrupted at two regions that are diametrically opposed to each other. In the region of the anti-rotation groove 62, the receiving portion 20 has a corresponding radial ridge 148, by which the maximum outer diameter 150 of the cross section of the receiving portion 20 is defined. In this case, the radial inner diameter 152 of the cross section of the push-fit 97 is smaller than the maximum outer diameter 150 of the receiving portion 20, but larger than the receiving portion diameter 154 of the cross section of the receiving portion 20 without considering the radial ridges 148. Thus, at least one axial anti-rotation groove 62 extends radially beyond the push-fit 97 and provides additional space there, particularly as a clearance space for the associated guide portion 61. Furthermore, the axially extending radial abutment region 144 extends parallel to and coaxially with the receiving portion 20, such that the support element 72 partially overlaps the receiving portion 20 with its cup wall 89 in the axial direction. Thus, in the axial extension, the axially overlapping region can also at least partially serve as the stroke space 146, thereby forming an axially compact cylinder body 40 (see Figure 1 ).

[0056] Furthermore, the push-in fit 97 and the upset portion 94, designed as an interference fit 98, achieve a stable and force-transmitting fixation of the support element 72 at the housing 18. This fixation allows the torque and moment generated during operation to be directly and stably transmitted to the housing 18 over a wide range and dissipated therefrom (e.g., Figure 1 and Figure 5 (As indicated by the arrows in the diagram). Rotation of the nut 66 moves the main shaft 64 and, consequently, the piston 22 coupled thereto, axially into the working chamber 42 along the pressure direction 75 (large arrow). This generates a reaction force, indicated by the small arrows and shown only schematically, which is transmitted axially, particularly to the piston 22 and the main shaft 64 coupled thereto, and via the nut 66, to the support 70 in the axial, radial, and oblique directions, and from there to the support element 72. The support element 72 transmits the reaction force radially, obliquely, and axially to the housing 18 through the push-in fit 97, where it is counteracted.

[0057] To optimize the available structural space in the housing 18, and especially in the housing side 30 which serves as the motor side and extends along the X direction 156 and Z direction 158, the two anti-rotation slots 62 and their slot center axes 160 are not arranged parallel to the housing side 162 adjacent to the two housing sides 30 and 35 and opposite to the memory 55, but rather arranged at an angle to it. Figure 5 As shown in detail, there exists a first imaginary plane 163, which includes the receiving axis 24 and extends parallel to the housing side 162 and the memory side 164 opposite to the housing side 162 (see [link]). Figure 6Furthermore, the central axis 160 of each slot is arranged such that it forms a second imaginary plane 165 with the axis 24 of the receiving portion, which intersects the first imaginary plane 163 at an angle 166. This angle 166 is approximately 30°.

[0058] Figure 6 The hydraulic assembly 12 in its assembled state is shown, with the view directed toward the housing side 30, which serves as the motor side. A mounting side 167 abuts the housing side 30, where the hydraulic assembly 12 is secured to a vehicle wall (not shown) via a mounting portion 168. Figure 6 The motor 14 is clearly visible being secured by two diametrically opposed fixing points 132. Here, fixing points 132 lie on an imaginary straight line 169, which forms an angle 172 of approximately 30° with the plane 170 containing the housing side 162. This angle 172 is approximately equal to angle 166, thus allowing the fixing points 132 to transmit force particularly well on the radially extended portions of the two anti-rotation grooves 62. Furthermore, the motor housing 122 is arranged on its housing side 30, which serves as the motor side, at the corner formed by the housing side 162 and the fixing side 167, enabling the radially extending flange 126 from the motor housing 122. Therefore, spaces are formed on the housing side 30 and within the housing 18 for other accommodating portions (not shown). The flange 126 requires a full circumference to surround a complete seal (not shown) between the flange 126 and the housing 18. Furthermore, Figure 6 The relevant lug 128 shown on the right extends downward in a particularly space-saving manner toward the housing side 162.

[0059] Figure 7 An embodiment of a pressure device 10, as a first type of pressure device 10 or a first class of pressure device 10, is shown above. This pressure device has: a receiving portion 20 having a first axial dimension 173, a support element 72 having a first protrusion 100, and a cover element 106 having a second protrusion 114, shown schematically. Here, the second protrusion represents the total protrusion 114 of the protruding element 120 formed by the cover element 106 and the support element 72. Furthermore, the motor housing 122, also shown schematically, and its associated first axial dimension 174 are also shown. Here, the first axial dimension 173 of the receiving portion 20 corresponds to the first housing thickness 176 of the housing 18 extending between the two housing sides 30, 35. The usable volume or pressure volume of the cylinder 40 is determined by the first axial dimension 173 of the receiving portion 20, the associated receiving portion diameter 154, and the cup-shaped cylinder head 36.

[0060] Furthermore, at least one of the associated axial anti-rotation grooves 62 has a first axial dimension of 178 (only in Figure 1(As shown in the diagram). Additionally, in the receiving portion 20, the radial sealing groove 44 is arranged at the first axial position 180, while the radial sealing groove 50 is arranged at the corresponding first axial position 182.

[0061] Compared to the first pressure device type 10, Figure 7 The second pressure device type 184, or second class of pressure device 184, is shown below. It has a larger volume of associated cylinder 40 and therefore greater power. Structurally, the second pressure device type 184 differs from the first pressure device type 10 only slightly. The design and fixing method of the support element 72 and its first protrusion 100, as well as the cover element 106 and the protrusion element 120 and its second protrusion 114, are identical. Therefore, the design of the total protrusion 114 extending from the housing side 30, which serves as the motor side, is identical. The identical protrusion 114 ensures that the motor shaft 78 engages with the transmission 76, more specifically, at the same depth in its sun gear, and the engagement depth from the transmission 76 to the motor 14 is also identical. This provides a unified motor interface for the various pressure device types 10, 184. If needed, a higher-powered motor 186 can be mounted at this unified interface, whose second axial dimension 190 of the motor housing 188 is structurally easier to make larger than the corresponding first axial dimension 174 of the first pressure device type 10.

[0062] Furthermore, the design and fixing method of the cup-shaped cylinder head 36 in both pressure device types 10 and 184 are the same. Therefore, the cylinder head 36 also has a uniform protrusion 37, through which a uniform interface is also formed on the housing side 35, which serves as the controller side, without affecting the circuit board of the corresponding associated controller 192.

[0063] Unlike the first pressure device type 10, the associated housing 18 of the second pressure device type 184 is designed with a larger second housing thickness 194. Correspondingly, the second axial dimension 196 of the receiving portion 20 associated with the second pressure device type 184 is larger than the first axial dimension 173. Furthermore, the associated axial anti-rotation groove 62 correspondingly has a second axial dimension (not shown), which is larger than the first axial dimension 178. Additionally, the second axial position 198 associated with the radial sealing groove 44 is arranged further away from the cylinder head 36 than the corresponding first axial position 180. Furthermore, the second axial position 200 associated with the radial sealing groove 50 is also arranged further away from the cylinder head 36 than the corresponding first axial position 182. Simultaneously, the larger second housing thickness 194 creates a receiving area 202 from the sealing groove 44 and the piston seal 46 disposed therein in the direction toward the cylinder head 36. The receiving area 202, together with the cylinder head 36, forms the working chamber 204 of the second pressure device type 184, which is larger than the working chamber 42 of the first pressure device type 10. The corresponding receiving portion diameter 154 is designed identically. Therefore, different plunger volumes or pressure device volumes are achieved simply by changing the housing thickness 176, 194 or the axial dimensions 173, 196 of the receiving portion 20. The cylinder block 40 is designed as a two-piece unit, wherein the cylinder head 36 has a consistently identical structure, while the receiving portions 20 have different axial dimensions 173, 196. Therefore, different braking systems can be designed cost-effectively using consistently identical closing elements, such as the cylinder head 36 and support element 72.

[0064] Figure 8 Details of the embodiment are shown, wherein the support element 72 is held in the housing 18 by a push-in fit 97 designed with a form fit 206. For this purpose, opposite to the cup bottom 86, the cup wall 89 is designed with at least one radially inclined, inwardly pointing hook 208 that forms a form fit into the housing 18. A contact surface 145 extending obliquely relative to the axis 24 of the receiving portion is formed by at least one hook 208, at which the support element 72 axially abuts. Additionally, a radial contact area 144 of the support element is formed by the cup wall 89 and each hook 208.

[0065] Figure 9A partial top view of the housing side 35, which serves as the controller side, is shown; the cylinder head 36, mounted above the receiving opening 34, is not shown. A radial groove 210 surrounds the receiving opening 34 and extends into the housing side 35, forming a housing shoulder 212. In the assembled state, the cylinder head 36 is press-fitted onto the housing shoulder 212, forming an interference fit at the inner wall 214 of the groove 210. This interference fit is slightly interrupted at two diametrically opposed locations by axial inflow and outflow portions 58, which are configured as axial openings in the groove 210. Piping sections 216 lead from each inflow and outflow portion 58 to the associated control valve 60 of the associated brake line 59.

[0066] Figure 10 Variations are shown, where... Figure 9 The difference is that one of the two inflow and outflow portions 58 has a kidney-shaped recess 218 that increases its cross-section. Here, the kidney-shaped recess 218 is connected to the memory 55 (not shown) so that the pressure medium flows in from the memory 55 by suction.

Claims

1. A pressure device (10, 184), particularly a pressure device for a hydraulic assembly (12) of a vehicle braking system, said pressure device having a piston (22) axially movable in a cylinder (40) and a motor (14, 186) selectively axially moving said piston (22) in two directions, wherein, The cylinder (40) is designed to have a receiving portion (20) arranged in a hydraulic housing (18), the receiving portion having a receiving opening (28) at its end (26) facing the motor (14, 186), the receiving opening being partially covered by a support element (72), wherein a component (73) coupled to the motor (14, 186) for power transmission is supported in the hydraulic housing (18) by the support element (72), and the support element (72) is held in the hydraulic housing (18). The characteristic feature is that the support element (72) is coupled to the hydraulic housing (18) by a push-in fit (97) to withstand the radial and axial forces generated during operation.

2. The pressure device according to claim 1, characterized in that, The push-in fit (97) is designed as an interference fit (98).

3. The pressure device according to claim 1 or 2, characterized in that, The push-in fit (97) is designed as a shape fit (206).

4. The pressure device according to any one of claims 1 to 3, characterized in that, The support element (72) is axially abutted against the hydraulic housing (18) by abutting surface (145), and in particular, the support element (72) has a radially extending flange (90) abutting against the abutting surface (145) and preferably is upset together with the material (92) of the hydraulic housing (18) radially outward, or is held by a clamping portion surrounding the flange (90) of the support element (72).

5. The pressure device according to any one of claims 1 to 4, characterized in that, The receiving portion (20) has at least one axial anti-rotation groove (62) to correspondingly receive a guide portion (61) extending radially from the piston (22), and the push-in engagement (97) is interrupted particularly in the region of the at least one axial anti-rotation groove (62).

6. The pressure device according to claim 5, characterized in that, The receiving portion (20) has a receiving portion axis (24) that extends perpendicularly to the two opposing housing sides (30, 35) of the hydraulic housing (18) and lies within a first imaginary plane (163) that extends parallel to the memory side (164) of the hydraulic housing (18) adjacent to the two housing sides (30, 35). The at least one axial anti-rotation groove (62) extends with its groove center axis (160) parallel to the receiving portion axis (24), wherein the groove center axis (160) and the receiving portion axis (24) lie within a second imaginary plane (165) such that the second imaginary plane (165) is rotated by an angle (166) of 10° to 50°, preferably 20° to 40°, and particularly preferably 30° about the receiving portion axis (24) relative to the first imaginary plane (163).

7. The pressure device according to any one of claims 1 to 6, characterized in that, The support element (72) is surrounded by the motor housing (122, 188) of the motor (14, 186), which is fixed to the hydraulic housing (18) by two fixing points (132) that are diametrically opposed to each other. In particular, the two fixing points (132) are located on an imaginary straight line (169) that forms an angle (172) of 10° to 50°, preferably 20° to 40°, and particularly preferably 30° with the plane (170) where the housing side (162) opposite to the memory side (164) is located.

8. The pressure device according to any one of claims 1 to 7, characterized in that, The receiving portion (20) has another receiving opening (34) at its end (32) opposite to the motor (14), the other receiving opening being closed by a cup-shaped cylinder head (36), and in particular, the receiving portion (20) has a radial sealing groove (44) between the axial anti-rotation groove (62) and the other receiving opening (34), in which a piston seal (46) surrounding the piston (22) is received, preferably such that the receiving portion (20), the cup-shaped cylinder head (36), and the The working chamber (42, 204) enclosed by the piston seal (46) and the piston (22) does not have a passage to the memory (55) to be arranged in the hydraulic housing (18), and in particular, in the receiving part (20), another radial sealing groove (50) is provided axially between the axial anti-rotation groove (62) and the radial sealing groove (44), and a radial guide groove (53) is arranged axially between the two sealing grooves (44, 50), the radial guide groove being connected to the pressure medium.

9. The pressure device according to claim 8, characterized in that, The working chambers (42, 204) are fluidly connected to a corresponding associated control valve (59) of the associated braking circuit via at least one axial inflow and outflow portion (58).

10. The pressure device according to claim 8 or 9, characterized in that, The pressure medium is pumped into the memory (55) by means of a recess (218) at at least one of the axial inflow and outflow portions (58) of the working chamber (42, 204) to increase the cross-section of the inflow and outflow portion (58).

11. The pressure device according to any one of claims 1 to 10, characterized in that, The support element (72) is a protruding element (120) adapted to be identical relative to the hydraulic housing (18) for various pressure device types (10, 184), and The receiving portion (20) is adapted to be designed with different axial dimensions (173, 196) for various pressure device types (10, 184).

12. The pressure device according to claim 11, characterized in that, The receiving portion (20) has at least one axial anti-rotation groove (62) to accommodate a guide portion (61) extending radially from the piston (22), wherein the at least one anti-rotation groove (62) is designed to have different axial dimensions (178) for various pressure device types (10, 184).

13. The pressure device according to claim 11 or 12, characterized in that, The receiving portion (20) has at least one radial sealing groove (44, 50) to accommodate piston seals (46, 52) respectively, wherein the at least one sealing groove (44, 50) is arranged in the receiving portion (20) at correspondingly associated different axial positions (180, 182, 198, 200) for various pressure device types (10, 184).

14. The pressure device according to any one of claims 11 to 13, characterized in that, The support element (72) is surrounded by the motor housing (122, 188) of the motor (14, 186), which is adapted to have different axial dimensions (174, 190) for various pressure device types (10, 184) depending on the motor power associated with the motor (14, 186).

15. The pressure device according to any one of claims 11 to 14, characterized in that, The receiving portion (20) has another receiving opening (34) at its end (32) opposite to the motor (14, 186), the other receiving opening being closed by a cup-shaped cylinder head (36), and the cylinder head (36) being adapted to be structurally identical for various pressure device types (10, 184).

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