Brake operating device

Abstract

The present invention relates to a braking operating device (68), particularly for a vehicle braking system, having a pump housing (18) having a housing opening (16) surrounded by a wall (22), wherein the housing opening (16) includes a housing axis (24), a piston (26) is axially movable in the housing opening (16) along the housing axis, and the pump housing includes a guide region (73) in which a guide element (70) is arranged between the wall (22) and the piston (26), wherein, in the braking operating device, an overhang (72) extending from the wall (22) into the housing opening (16) is provided axially next to the guide region (73), and the guide element (70) axially abuts against the overhang.

Description

Technical Field

[0001] This invention relates to a braking operating device, particularly for a vehicle braking system, comprising a pump housing having a housing opening surrounded by a wall, wherein the housing opening includes a housing axis and a guide region, a piston is received in the housing opening in a manner movable along the housing axis, and a guide element disposed between the wall and the piston is received in the guide region. Furthermore, this invention relates to the application of this braking operating device in a vehicle braking system. Background Technology

[0002] This type of vehicle braking system is used to reduce the speed of vehicles, such as passenger cars (PKW) and trucks (LKW). For this purpose, hydraulic braking systems are mostly used, which also function as anti-lock braking systems (ABS) and / or electronic stability programs (ESP). Here, regulated braking pressure is provided in the subordinate braking circuits by means of a hydraulic unit and hydraulic fluid. To generate braking pressure, a pedal-operated master brake cylinder is provided, which is usually connected to two braking circuits, each with brake lines through which hydraulic fluid can flow. When the driver operates the brake pedal, the mechanical force applied is converted into hydraulic pressure by increasing the pressure on the hydraulic fluid. This force then acts as a braking force on the subordinate wheel brakes.

[0003] Known master brake cylinders or pressure-generating cylinders typically have a brake operating device, which is mostly designed as a block or a solid body. In this case, a housing opening with a housing axis is formed by means of a hole in the block, in which the cylinder and piston are arranged. The piston is axially moved within the cylinder or housing opening by the brake pedal, and the piston is sealed relative to the outside in the housing opening by at least one sealing ring. Furthermore, the piston is guided during its translational movement along the housing axis by guide elements arranged radially around the piston. Here, the guide elements are particularly used to assist in overcoming the lateral forces that occur during operation, mainly when the brake pedal is operated. Such a brake operating device is known from DE 10 2015 207 634 A1. Summary of the Invention

[0004] This invention relates to a brake operating device or brake request specification device, particularly for a vehicle braking system. The brake operating device or brake request specification device has a pump housing with a housing opening surrounded by a wall. This housing opening includes a housing axis, in which a piston is axially movably received. The pump housing includes a guide region accommodating a guide element disposed between the wall and the piston. Here, axially adjacent to the guide region, a raised portion extending from the wall into the housing opening is provided in the housing opening, and the guide element axially abuts against this raised portion.

[0005] Therefore, the superelevation section extends from the wall and into the pump housing or the housing opening of the housing, specifically into the cavity formed by the wall. Furthermore, the superelevation section is particularly positioned directly adjacent to the guide area. If the guide element housed in the guide area axially abuts against the superelevation section, the axial force acting on the guide element during installation and operation is borne by the superelevation section. In this manner, the force is transmitted from the superelevation section to the housing. Compared to the guide element, the housing is significantly larger and comprises more material, thus the axial force acting on the guide element is borne by the housing in a manner distributed over a wide range. This force distribution acts particularly stably and gently on the associated components. The axial forces present are particularly the axially acting installation force, the frictional force acting when the piston moves into the housing opening, and the working force due to hydraulic pressure. That is, a braking operating device is thus realized according to the invention, by which the forces occurring during the installation and operation of the piston pump can be borne by the housing itself in a particularly good distributed manner. Furthermore, the piston, guided by the guide element abutting against the superelevation section, gains additional stability. Therefore, the guide element has a smaller diameter and shorter length compared to conventional guide elements, which is sufficient. In particular, a lightweight braking operating device has been achieved.

[0006] Additionally, a housing opening is provided by the superelevation or protrusion according to the invention, which has a substantially similar cross-section, particularly before and after the superelevation, in the axial direction. The cross-section of the housing, and consequently the inner cavity, is reduced only in the region of the superelevation. This results in a relatively large inner cavity, particularly axially, formed within the superelevation, providing space for other pumping components. Preferably, a sealing element can be positioned within this inner cavity.

[0007] Preferably, the superelevation section is designed as a bridging section. This bridging section extends radially into the housing opening and is configured to be relatively flat in the axial direction. It has been determined that this bridging section, despite its very small axial extension, is surprisingly very stable to the resulting contact forces.

[0008] Furthermore, preferably, the superelevation portion and especially the bridging portion have a substantially flat surface on the side facing the guide element, specifically the outer side, for abutting the guide element. Here, the guide element can abut or rest against the superelevation portion with particular stability and good force transmission. Force transmission is particularly favorable in that the guide element can abut or rest against the superelevation portion, preferably on its entire abutting side, using its abutting side facing the superelevation portion.

[0009] Furthermore, preferably, the superelevation section is designed to extend transversely to the shell axis, and more preferably approximately perpendicular to the shell axis. This achieves a particularly uniform force distribution while providing advantageous space for other structural elements.

[0010] Furthermore, the housing is preferably designed as a block shape, thereby bearing the forces that arise in a particularly good manner. Here, it is especially preferred that the housing of the main brake cylinder be integrated into the hydraulic block. This results in a very compact and space-saving braking system.

[0011] Advantageously, according to the invention, the superelevation section is designed as an integral part of the housing. This results in the superelevation section being arranged particularly stably on the housing, and the force transmission from the superelevation section to the housing is particularly high.

[0012] Furthermore, according to the invention, the housing opening advantageously includes a sealing region in which a sealing element disposed between the wall and the piston is accommodated. Here, the sealing region is arranged on the side of the elevation opposite to the guide region, so that the elevation is axially located between the guide region and the sealing region. If the sealing element is accommodated in the sealing region, the sealing element is radially arranged between the wall and the piston and axially arranged on the side of the elevation opposite to the guide element, specifically the sealing side. Here, the sealing side of the elevation is the side facing the inner cavity of the housing, which has an inner surface against which the sealing element axially abuts. Thus, the elevation is axially positioned between the sealing element and the guide element, directly bearing the corresponding axial force and transmitting this axial force to the housing. For this purpose, the sealing element is preferably designed to have a sealing ring that completely surrounds the piston radially. This achieves a particularly good sealing effect.

[0013] Preferably, the braking operating device according to the invention is a component of the master brake cylinder. Here, particularly when the piston returns due to the release of the brake pedal, an axial force acts on the sealing element from the inner cavity towards the superelevation. This force is borne by the superelevation and transmitted to the housing. By bearing this force in this way, the sealing element is protected and stabilized during operation. Thus, a particularly reliable and long-lasting sealing effect of the braking operating device is achieved in the master brake cylinder. During the installation of the braking operating device and during operation, an axial force from the outside towards the inner cavity occurs due to the forward movement of the piston, particularly when the brake pedal is operated. The corresponding installation force, working force, and frictional force are also borne by the superelevation.

[0014] Preferably, the guiding element is designed to have a guide ring. This guide ring is arranged radially around the piston, that is, in the installed state, it completely surrounds the piston's circumference. This results in the piston being guided particularly compactly, stably, and uniformly.

[0015] Furthermore, according to the invention, the guide element has a radial outer surface designed with a transition fit that positions it axially toward the superelevation. This transition fit is particularly a radial press fit that orients the guide element coaxially with respect to the housing opening. This makes targeted installation easier when pressing the guide element toward the superelevation. Additionally, this transition fit provides a certain gap between the guide element and the housing wall. For this purpose, the transition fit is preferably designed with a reduced diameter portion of the guide element toward the superelevation, particularly preferably as a radially inward chamfer or step.

[0016] Furthermore, according to the invention, the guide element has a radially inner surface designed with a bevel positioned axially toward the superelevation. That is, the guide element tapers radially inward toward the superelevation. Thus, deformation generated during the pressing of the guide element into the cavity is absorbed within the guide element. Consequently, the guide region of the guide element facing the piston does not deform in an undesirable braking manner after pressing; instead, such deformation is prevented by means of the bevel.

[0017] Advantageously, according to the invention, the guide element further has a radially outer surface designed with a radially inwardly stepped portion positioned axially away from the superelevation portion. Through this stepped portion, a shoulder is provided on the guide element axially opposite to the abutment side, the shoulder being positioned in the braking operating device opposite to the superelevation portion. Preferably, other structural elements on the guide element can be arranged or disposed on this shoulder in a space-saving manner. Particularly preferably, the guide element is compactly held on a housing by means of a molded housing at the shoulder.

[0018] To this end, according to the invention, advantageously, at least one section is provided through which the stepped portion of the guide element and the housing are molded together when the guide element is received in the guide region of the housing opening. Specifically, each section comprises material, which is molded to fit the shape of the guide element onto the shoulder obtained through the stepped portion and onto the subordinate interface of the housing. At this time, the subordinate interface is located at the opening of the housing opening, into which the piston and guide element are introduced. This segmental molding, combined with the superelevation according to the invention, is sufficient to resist hydraulic pressure occurring within the cavity of the housing. By means of the superelevation, the hydraulic pressure is borne through the superelevation and thus directly within the housing. Therefore, the molded portion of the guide element is not subjected to load.

[0019] Here, individual segments are preferably designed with material introduced from the outside. This allows for flexible molding according to the desired material properties. Particularly preferably, the individual segments are formed from the material of the housing itself at the interface of the housing. Therefore, molding on the individual segments causes the housing to deform accordingly, thereby achieving a simple and material-saving installation. Furthermore, it is preferable to provide at least two segments, through which stable partial molding is achieved. Particularly preferably, four segments are provided, especially arranged at equal distances from each other. Thus, segmental molding that is both material-saving and sufficiently stable is achieved by means of partial shape fit.

[0020] Advantageously, according to the invention, at least one section is designed as a point. This establishes a particularly space-saving connection between the guide element and the housing.

[0021] Furthermore, according to the invention, preferably, at least one cavity is provided radially in the pump housing, adjacent to the guide region and outside the housing opening. Here, the individual cavity is preferably arranged spaced apart from the housing opening. In the block-shaped housing and the hole forming the housing opening, the individual cavity is in particular a notch arranged radially relative to the housing opening and extending axially parallel to the housing axis. If the guide element is housed in the guide region, then the at least one cavity is arranged radially around the guide element. Thus, the guide element is radially partially surrounded by at least one cavity. For this purpose, the individual cavity is preferably eccentrically, and particularly preferably concentrically, relative to the housing axis. Thus, the individual cavity serves as a buffer for the guide element, by which the buffer intercepts radially outward forces and thereby protects the guide element.

[0022] Advantageously, according to the invention, a single cavity is provided in the region of a subordinate ball valve, which is arranged in the housing around the guide region of the housing opening. Preferably, at least two ball valves are provided, which are eccentrically arranged around the guide region of the housing opening. Here, the single ball valve, by means of its subordinate ball, deforms in the guide region, and this deformation is absorbed and compensated by at least one cavity in the housing. Thus, this deformation does not intersect with the diameter of the center of the guide element, thereby avoiding the negative impact of the deformation on the guide region.

[0023] Furthermore, the present invention relates to the application of this type of braking operating device in or within the master brake cylinder of a vehicle braking system, wherein, in particular, the master brake cylinder is integrated into the hydraulic block of a hydraulic unit. This results in a particularly lightweight, space-saving, and cost-effective vehicle braking system, while also achieving the advantages described above for the braking operating device. Attached Figure Description

[0024] The embodiments of the solution according to the present invention will now be explained in detail with reference to the accompanying schematic diagrams. The diagrams show:

[0025] Figure 1 A cross-sectional view of a hydraulic scheme having a main brake cylinder based on the present invention is shown.

[0026] Figure 2 It shows that according to Figure 1 A longitudinal section view of a portion of the main brake cylinder.

[0027] Figure 3 It shows Figure 2 Detail III in

[0028] Figure 4 A partial longitudinal sectional view of a first embodiment of a braking operating device according to the present invention without a piston is shown.

[0029] Figure 5 It shows that according to Figure 4 Details V,

[0030] Figure 6 The following is shown: A piston-based... Figure 4 View VI,

[0031] Figure 7 It shows that according to Figure 6 Section VII-VII,

[0032] Figure 8 A second embodiment of the braking operating device according to the present invention is shown. Figure 6 The view, and

[0033] Figure 9 It shows that according to Figure 8 Section IX-IX. Detailed Implementation

[0034] Figures 1 to 3 The master brake cylinder 10 and the subordinate brake operating device 11 of the hydraulic vehicle braking system (not shown in detail) are illustrated schematically, as if the vehicle braking system were used in a braking system with anti-slip adjustments such as ABS and ESP. Here, the master brake cylinder 10 is integrated into a square hydraulic block 12 made of aluminum, shown only schematically. There is a so-called One-Box system and, consequently, an integrated brake control system (IPB) that is directly mounted on the front bulkhead of the vehicle (not shown).

[0035] The master brake cylinder 10 is arranged in a master brake cylinder bore that is parallel to the lateral side 14 of the hydraulic block 12 and serves as a housing opening 16. The pump housing 18 is realized through the housing opening 16 and the hydraulic block 12, in which the housing opening 16 forms an inner cavity 20, which is surrounded by a wall 22 and has a housing axis 24.

[0036] The housing axis 24 is aligned with the piston axis subordinate to the piston 26. Here, the piston 26 is hinged to a piston rod 28 outside the pump housing, specifically outside the housing 18, and this piston rod is coupled to a brake pedal 30 that can be operated by a vehicle user. When the brake pedal 30 is operated, the piston 26 moves mechanically along the housing axis 24 within the housing opening 16 by means of the piston rod 28. Here, the piston 26 is a so-called rod piston or primary piston, supported by a compression spring 29 on a second piston 32 arranged axially after the piston 26. Furthermore, the second piston 32 is axially movable and supported by a second compression spring 34 on a housing side 36 opposite the piston 26 at its end. The piston 32 is also referred to as a high-pressure piston or secondary piston. Thus, a piston pump 33 is formed having two brake cylinders arranged sequentially in the axial direction, with the master brake cylinder 10 designed to be connected in series.

[0037] This design necessitates the operation of a dual-circuit braking device (not shown). For this purpose, a first pressure chamber 38 exists between the two pistons 26, 32 and the housing 18. Hydraulic fluid, or other fluid, is drawn into the pressure chamber from a reservoir (not shown) via a conduit 40. This fluid is then pumped into the first braking circuit via another conduit 42. A second pressure chamber 44, located between the piston 32 and the housing side 36, is equipped with corresponding conduits 40 and 42, through which fluid is supplied to the second braking circuit. When the brake pedal 30 is actuated, the piston 26 is pushed into the housing opening 16, thereby generating hydraulic pressure in the first pressure chamber 38. This pressure pushes the piston 32 toward the housing side 36, thereby generating hydraulic pressure in the second pressure chamber 44.

[0038] The two pistons 26 and 32 are sealed within the inner cavity 20 by radially surrounding sealing rings 46. For this purpose, each sealing ring 46 is arranged in a subordinate annular groove 48 in the wall 22. Furthermore, an additional sealing element 50, designed as a sealing ring, is arranged radially around the piston 26 in the direction towards the piston rod 28. The sealing element 50 is received in an annular cavity 52, which is realized by means of an annular step 54 extending radially outward from the wall 22. Here, the sealing ring 46 immediately adjacent to the step 54 is referred to as the first insulating seal, and the sealing element 50 itself is referred to as the second insulating seal.

[0039] Furthermore, in the braking operating device 11, a guide element 56 is provided axially outside the sealing element 50, which radially surrounds the piston 26 as a guide ring. The guide element 56 is used to withstand the axial and lateral forces that occur during operation. The lateral force mainly occurs when the brake pedal 30 is operated, because the brake pedal 30 causes the piston rod 28 to move in a circular trajectory at its end opposite to the piston 26. The axial force is mainly caused by hydraulic pressure.

[0040] Here, the guide element 56 is axially directly arranged on the sealing element 50 using its contact surface 58 in the braking operating device 11. Furthermore, the guide element 56 axially abuts against another stepped portion 60 of the housing opening 16 using a small area of ​​its contact surface 58. Here, compared to the stepped portion 54, the wall 22 of the inner cavity 20 is further radially offset outward by the other stepped portion 60. Additionally, a surrounding, radially outwardly extending edge 62 is provided on the guide element 56, which is fixed to the housing 18 by molding (filling). The molding portion 64 is a plastically deformed portion of the material of the housing 18 surrounding the opening 66 of the housing opening 16, which overlaps the edge 62. Thus, the guide element 56 is axially held at or within the housing 18.

[0041] exist Figures 4 to 7 An embodiment of the braking operating device 68 is shown, illustrated with the piston 26 partially absent for better visibility. Here, unlike the braking operating device 11, a raised section 72 is provided in the inner cavity 20, on which the guide element 70 axially abuts. For this purpose, the guide element 70 is accommodated in a guide region 73 that extends from the raised section 72 toward the opening 66 in the housing opening 16. Here, unlike the stepped section 60, the raised section 72 extends radially inward from the wall 22 into the housing opening 16. Furthermore, the raised section 72 is designed as a flat member in the form of an annular bridging portion, extending laterally at right angles to the housing axis 24 into the inner cavity 20 and integrally designed with the housing 18.

[0042] Here, the elevated portion 72 has an outer side 74 that is axially opposed to the inner cavity 20, and the guide element 70 axially abuts against this outer side using its abutment surface 76. Both the abutment surface 76 and the outer side 74 are designed as annular surfaces and are also substantially flat. Furthermore, the abutment surface 76 extends entirely along the abutment side 78 of the guide element 70 facing the elevated portion 72. Therefore, compared to the small area of ​​the abutment surface 58 of the guide element 56 on the stepped portion 60, a significantly larger abutment area of ​​the guide element 70 is achieved on the elevated portion 72. Consequently, the guide element 70 can withstand axial forces over a larger area and correspondingly transmit these forces to the block-shaped housing 18 over a larger area.

[0043] Opposite to the outer side 74 and facing the inner cavity 20, the elevated portion 72 has an annular inner or side portion 80, which is designed to be as flat as possible, and is opposite to the guide element 70. A sealing region 82 for the housing opening 16 is provided axially between the side portion 80 and the stepped portion 54, and a sealing element 50 designed as a sealing ring and a lip seal is arranged in this sealing region. Thus, on the side portion 80, the axial force acting from the inside to the outside is transmitted through the sealing element 50 to the elevated portion 72 and from the elevated portion to the housing 18.

[0044] Furthermore, the guide element 70 has a radially outer surface 84 on its periphery, which has a transition fit portion 86 in the direction of the abutment surface 76 of the guide element and further in the direction of the outer side 74 of the superelevation portion 72. Here, the transition fit portion 86 has a first radially inwardly inclined surface 90 starting from the peripheral surface 88 of the guide element 70 in the direction of the superelevation portion 72. Immediately following the first inclined surface 90, a peripheral surface 92 with a smaller diameter than the peripheral surface 88 is provided, and immediately following the peripheral surface 92 is a second radially inwardly inclined surface 94. In addition, the guide element 70 includes a radially inner surface 96 in the radial interior, which is designed to taper towards the superelevation portion 72 by a chamfer 98. The chamfer 98 has a radially outwardly inclined surface 102 starting from the inner peripheral surface 100.

[0045] To install the guide element 70 onto the housing 18, in the first installation step, the guide element 70 is introduced at the opening 66 and pressed into the housing opening 16. At this time, the transition fit 86 facilitates the targeted introduction through a corresponding clearance. During the continued pressing process, the guide element 70 is pressed into the inner cavity 20 until the guide element 70 abuts against the outer side 74 of the elevation portion 72. Excessive force at this time is borne by the elevation portion 72 of the housing 18. Furthermore, the deformation generated by this pressing process is absorbed by the chamfer 98.

[0046] Furthermore, the radially outer surface 84 of the guide element 70 has a radially inward stepped portion 104 that faces away from the super-high portion 72. Through the stepped portion 104, a recessed shoulder 106 is formed on the guide element 70 opposite to the abutment surface 76, whereby the recessed shoulder extends radially around the entire periphery of the guide element 70.

[0047] To proceed with the installation of the guide element 70, in the second installation step, the shoulder 106 or step 104 is molded together with a plurality of point-like segments 108 of the housing 18. In this embodiment, four segments 108 are provided, which are evenly distributed on the circular opening 66 in cross-section of the housing opening 16. Figure 6To this end, pressure is applied in sections on the opening 66 by the molding tool 110 to the material of the housing 18, causing the material on each section 108 to deform onto the shoulder 106. Figure 7 That is, the shoulder 106 is segmentally overlapped by the deformed material of the housing 18. By means of this segmental molding, the guide element 70 is held on the housing 18 in the housing opening 16.

[0048] During installation, an axial installation force 112 occurs in the direction pointing from the outside towards the superelevation part 72 during clamping and molding. Figure 7 The mounting force 112 is borne by the superelevation section 72 and transmitted to the housing 18. Furthermore, friction occurs when the brake pedal 30 is operated, causing the piston rod 28 and piston 26 to move forward. This friction, like the mounting force 112, also acts axially from the outside onto the superelevation section 72 and is transmitted from the superelevation section 72 to the housing 18. That is, the reduced force acts from the outside inward onto the guide element 70 and the sealing element 50.

[0049] The friction generated during the return stroke of the piston 26 due to the release of the brake pedal 30 creates an axial force 114 acting from the inside out, specifically from the inner cavity 20 towards the superelevation section 72. This force 114 also includes a working force generated by hydraulic pressure. The force 114 acts on the sealing element 50 abutting against the superelevation section 72, is transmitted through the sealing element 50 to the superelevation section 72, and from there to the housing 18. Thus, the force 114 acting outward on the guide element 70 and the section 108 is also reduced by means of the superelevation section 72.

[0050] It has been shown that this force transmission via the superelevation section 72 to the entire shell 18, and the resulting reduction in force in the axial direction, is particularly safe for the components and thus saves material. Therefore, the sealing element 50 is held and protected by the superelevation section 72, and thereby reliably seals the cabin as an additional seal. Thus, the sealing element 50, as a second insulating seal, becomes part of the extended sealing scheme for the IBP. At this point, the sealing element 50 provides a reliable additional safety seal, by which hydraulic fluid contamination of the cabin interior is prevented in the event of leakage caused by a potentially damaged first insulating seal.

[0051] Furthermore, the described segmental molding, and thus molding the housing 18 and guide element 70 only partially together, is sufficient to stably hold the guide element 70 within the housing opening 16. Additionally, the guide element 70 has a smaller press-in section 116 and a smaller diameter 117 compared to the guide element 56, which is also sufficient. Thus, a particularly space-saving and cost-effective braking operating device 68 is achieved while reducing material weight.

[0052] Figure 8 and Figure 9 One embodiment illustrates a braking actuation device 68, in which three ball valves 118 are arranged eccentrically relative to the housing axis 24 at the periphery of the housing opening 16 or interface. Each ball valve 118 includes a ball 120, which is axially locked in a channel 122 arranged in the housing 18 at the height of a guide region 73 and radially locked near the guide region 73. This ball locking or ball valve 118 causes deformation in the guide region 73 of the housing opening 16.

[0053] To withstand any such deformation, cavities 124 are provided radially outside the housing opening 16 and axially at the height of the guide region 73, and respectively in the region of the individual ball valve 118. Thus, the individual cavities 124 are arranged radially next to the guide region 73 on the periphery of the subordinate passage 122 of the ball valve 118.

[0054] Thus, each cavity 124 is located within the compression region of the guide element 70 and the subordinate ball valve 118. Through the cavity 124, the deformation of the housing 18 caused by the subordinate ball valve 118 has no effect on the fit of the guide element 70 in the housing opening 16. Ultimately, the deformation borne by the cavity 124 does not intersect with the diameter of the center of the guide element 70. This avoids damage to the guidance between the piston 26 and the guide element 70.

[0055] To manufacture each cavity 124, a milling operation is performed after the interface of the metal block used as the housing 18 is machined. During this operation, additional material is removed axially at the height of the guide region 73 relative to the housing opening 16, thereby forming a single cavity 124. Thus, the cavity 124 is designed as a notch.

Claims

1. A brake operating device (68) for a vehicle braking system, the brake operating device having a pump housing (18) having a housing opening (16) surrounded by a wall (22), wherein, The housing opening (16) includes a housing axis (24) and a guide region (73). A piston (26) is axially movable within the housing opening (16) along the housing axis. A guide element (70) arranged between the wall (22) and the piston (26) is accommodated in the guide region. The characteristic feature is that an overhang (72) extending from the wall (22) into the housing opening (16) is provided axially beside the guide region (73). The guide element (70) utilizes its abutment side facing the overhang to adjust... The guide region is axially directly abutted against the superelevation section, and the guide region extends from the superelevation section (72) toward the opening (66) surrounding the housing opening (16), the housing opening (16) including a sealing region (82) in which a sealing element (50) is arranged between the wall (22) and the piston (26), and the sealing region (82) is arranged on the side (80) of the superelevation section (72) opposite to the guide region (73), by means of the superelevation section, the hydraulic pressure is borne through the superelevation section and thus directly in the housing.

2. The braking operating device according to claim 1, characterized in that, The super-high section (72) is designed as an integral part of the pump housing (18).

3. The braking operating device according to claim 1 or 2, characterized in that, The guide element (70) has a radial outer surface (84) designed to have a transition fit (86) that is axially positioned toward the superelevation (72).

4. The braking operating device according to claim 1 or 2, characterized in that, The guide element (70) has a radial inner surface (96) designed with chamfers (98) positioned axially toward the superelevation (72).

5. The braking operating device according to claim 1 or 2, characterized in that, The guide element (70) has a radial outer surface (84) designed to have a radially inward stepped portion (104) positioned axially away from the superelevation portion (72).

6. The braking operating device according to claim 5, characterized in that, At least one section (108) is provided, through which the stepped portion (104) of the guide element (70) and the pump housing (18) are molded together when the guide element (70) is accommodated in the guide area.

7. The braking operating device according to claim 6, characterized in that, The at least one segment (108) is designed as a dot.

8. The braking operating device (68) according to claim 1 or 2, characterized in that, At least one cavity (124) is provided radially in the pump housing (18) beside the guide area (73) and outside the housing opening (16).

9. The application of a braking operation device (68) according to any one of claims 1 to 8 in the master brake cylinder (10) of a vehicle braking system.

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