Adjustable damping valve device for shock absorber

Abstract

The invention relates to an adjustable damping valve device for a vibration damper, comprising a damping valve housing in which a pilot valve for hydraulically controlling a main stage valve is arranged, the invention relates to a damping valve device for a vibration damper, comprising a damping valve housing which is hydraulically connected to a working chamber on the piston rod side of a working cylinder of the vibration damper and to a working chamber remote from the piston rod, the damping valve device comprising a check valve arrangement for rectifying a control volume flow from the working chamber of the working cylinder to a pilot valve, the pilot valve body of the pilot valve has a first pressure-bearing surface for the flow from the working chamber on the piston rod side and a second pressure-bearing surface for the flow from the working chamber away from the piston rod.

Description

Technical Field

[0001] The invention relates to an adjustable damping valve arrangement for a shock absorber according to the preamble of claim 1 . Background Art

[0002] Document DE 44 18 972 A1 relates to an adjustable damping valve arrangement comprising a valve housing located on the piston rod of a shock absorber. The functional advantage of this damping valve arrangement is that a single pilot valve is used to actuate the main stage valve, with flows originating from both the piston rod-side working chamber and the working chamber remote from the piston rod.

[0003] To this end, the damping valve arrangement has a total of four non-return valves, which ensure that the volume flows originating from the piston rod-side working chamber and the working chamber remote from the piston rod to the pilot valve are rectified, and that the return flow chamber of the pilot valve flows out to both working chambers. The non-return valves that switch the inflowing fluid are formed on or in the main stage valve body.

[0004] Adjusting the operating characteristics of the entire damping valve arrangement also involves rectifying the volume flow of the pilot valve, since the pilot valve also acts on the common mainstage valve. Although it is possible to provide pressure-bearing surfaces of different sizes on the mainstage valve for the two flow directions from the working chamber, the resulting ratio of damping forces in the tension direction to the compression direction may not be sufficient for some applications. Summary of the Invention

[0005] The object of the present invention is to provide a damping valve arrangement having a pilot valve which acts in both operating directions of the shock absorber, wherein the damping force ratio during alternating flow through the damping valve arrangement should be increased.

[0006] This object is achieved in that the pilot valve body of the pilot valve has a first pressure-bearing surface for the flow from the working chamber on the piston rod side and a second pressure-bearing surface for the flow from the working chamber remote from the piston rod, wherein the pilot valve has a first control chamber for the first pressure-bearing surface and a second control chamber for the second pressure-bearing surface, the two control chambers being hydraulically separated.

[0007] By using two pressure-bearing surfaces for different flow directions through the damping valve arrangement, a significant damping force characteristic effect can be achieved with a relatively small installation space. The achievable difference between the damping force level during an extended piston rod movement and the damping force level achievable during a retracted piston rod movement is significantly greater than if only the pressure-bearing surface on the main stage valve were used for this purpose. The control chamber can also be the working chamber of the shock absorber.

[0008] For a throughflow from one of the two working chambers, the first and second pressure-bearing surfaces are loaded, and for a throughflow from the other of the two working chambers, only the first pressure-bearing surface is loaded.

[0009] Preferably, the pilot valve body has two functional sections that can move relative to each other, which together radially define the first pressure-bearing surface on the pilot valve body. The main advantage of this structural form is that it simplifies the assembly of the pilot valve and improves its functional reliability.

[0010] Thus, one of the functional sections is formed by a control rod having a control surface acted upon by the pressure in the first control chamber. The control rod can interact with a known disk-shaped valve body as the second functional section of the pilot valve.

[0011] In another advantageous embodiment, the control rod for the pilot valve has a second pressure-bearing surface, which is loaded by the pressure in the second control chamber of the pilot valve. This second pressure-bearing surface can, for example, be used to connect two functional sections of the pilot valve to each other using the pressure in the control chamber.

[0012] Alternatively, it may be provided that the radial extent of the first pressure-bearing surface is determined by the relative axial position of the two functional sections. If, for example, the second pressure-bearing surface is oriented opposite to the lifting direction of the disk-shaped valve body as the second functional section, a separation movement may occur between the two functional sections when pressure is applied to the second pressure-bearing surface, thereby changing the radial extent of the first pressure-bearing surface.

[0013] A particularly space-saving design of the pilot valve is characterized in that a functional section is guided in an axially displaceable manner in the main stage valve body.

[0014] In a structural alternative, it is possible that a functional section which is axially displaceable in the main stage valve body extends axially through the main stage valve body in the compression direction toward one of the working chambers and has a surface which is acted upon by the pressure generated in the working chamber.

[0015] For the defined positioning of the axially displaceable control rod, a prestressing spring connects the two functional sections of the pilot valve body to one another.

[0016] It may also be provided that the pilot valve has three control chambers, wherein when fluid flows from the working chamber into the pilot valve, at least two of the control chambers are subjected to pressure in the lifting direction of the pilot valve. For both flow directions through the damping valve arrangement, a hydraulic pressure is provided using the third control chamber, which moves the control rod toward the disk-shaped valve body and connects it thereto.

[0017] In order to simplify the flow paths within the damping valve arrangement, provision can also be made for the control chamber for the main stage valve body to be connected to the two control chambers of the pilot valve.

[0018] In order to avoid a hydraulic short circuit through the pilot valve, the control chamber of the main stage valve and the second control chamber of the pilot valve are separated by a check valve which blocks a flow from the control chamber of the main stage valve towards the second control chamber of the pilot valve. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] The present invention will be explained in more detail with reference to the following description of the accompanying drawings.

[0020] in:

[0021] Figure 1 is a cross-sectional view of the damping valve assembly;

[0022] Figures 2 to 4 yes Figure 1 Detailed illustrations of various embodiments of the main-stage valve body are shown;

[0023] Figure 5 yes Figure 1 Alternative implementations of

[0024] Figure 6 yes Figure 4 Detailed diagram of

[0025] Figure 7 is located according to Figure 1 and Figure 5 Detailed view of the check valve assembly downstream of the pilot valve is shown. DETAILED DESCRIPTION

[0026] Figure 1 1 is a sectional view of an adjustable damping valve arrangement 1 for a shock absorber 3. In this exemplary embodiment, the damping valve arrangement 1 is shown in a damping valve housing 5 located on an axially displaceable piston rod 7 within a working cylinder 9 of the shock absorber 3. However, the damping valve housing 5 and the damping valve arrangement 1 can also be arranged spatially outside the shock absorber 3 and hydraulically connected, for example, via a line or hose connection.

[0027] The damping valve arrangement 1 comprises an electromagnetic actuator 11 having an excitation coil 13 and an armature 15 , the end of which acts on a pilot valve body 17 of a pilot valve 19 . The force of the excitation coil 13 acts in opposition to at least one return spring 21 .

[0028] The pilot valve 19 serves to hydraulically control a main stage valve 23 , through which a working chamber 25 on the piston rod side and a working chamber 27 remote from the piston rod in the working cylinder 9 are connected to one another. Figure 1The diagram shows radial connecting channels 29 within the valve housing ring, which is part of the damping valve housing 5 . These connect the piston rod-side working chamber 25 to the main stage valve 23 . Passive damping valves 33 and 35 are arranged between the working chamber 27 remote from the piston rod and the main stage valve 23 . Each passive damping valve serves a flow direction through the damping valve arrangement 1 . These two passive damping valves 33 and 35 are optional. Regardless of the working direction of the piston rod 7 within the shock absorber 3 , a volume flow of damping medium is discharged from the working cylinder 9 via the connecting channel 29 , the main stage valve 23 , and the two passive damping valves 33 and 35 . This volume flow determines the damping force. Furthermore, the sealed piston 36 , as a functional section of the damping valve housing 5 , serves to spatially separate the two working chambers 25 and 27 .

[0029] The main stage valve 23 comprises a main stage valve body 37 and a main stage valve seat surface 39 formed by a valve ring 41 within the valve housing ring 31 (see FIG. Figure 2 The main-stage valve body 37 is guided axially displaceably in the stepped opening 43 of the valve housing ring 31 . The main-stage valve body 37 is sealed against the inner circumferential surface 43A of the stepped opening 43 . The main-stage valve body 37 , a portion of the circumferential surface 43A, and the bottom 43B of the stepped opening 43 form a control chamber 45 for the main-stage valve 23 . This control chamber 45 is connected to the radial connection channel 29 via at least one first throttle channel 47 , wherein, due to the throttling function of the throttle channel 47 , there is a pressure drop between the pressure in the connection channel 29 and the pressure in the control chamber 45 . The pressure in the control chamber 45 exerts a pressing force on the main-stage valve body 37 , which acts as a closing force for the main-stage valve 23 .

[0030] The main-stage valve body 37 has a valve pin 49 that points toward the pilot valve 19 and, at its end, has a pilot valve seat surface 51 for the disk-shaped pilot valve body 17. The valve pin 49 is hollow and has at least one radial connection opening 53 leading to an axial channel, the pressure in which is equal to the pressure in the first control chamber 45. It can also be provided that the connection opening 53 performs a throttling function and thus a pressure drop exists between the control chamber 45 of the main-stage valve body 37 and the axial channel.

[0031] For the main stage valve, the axial passage forms a second control chamber 55 which exerts a second closing force on the main stage valve body 23. For the pilot valve 19, the axial passage forms a first control chamber 57 which has a pressing force component in the lifting direction of the pilot valve 19.

[0032] At least one connecting channel 63 extends within the mainstage valve body 37. This connecting channel has a throttling function similar to that of the first throttle channel 47 and connects a connecting chamber 65 of the damping valve arrangement 1 with the first control chamber 45. Consequently, the connecting chamber 65 is also connected to the first control chamber 57 of the pilot valve 19. To prevent a hydraulic short circuit through the first control chamber 45, the throttle channel 47 and the connecting channel 63 are each provided with a nonreturn valve disk 67, 69 that opens toward the control chamber 45 of the mainstage valve body 37.

[0033] In the present embodiment of the damping valve arrangement 1, the pilot valve body 17 has a first pressure-bearing surface D1 for flow through the connection channel 29 and the throttle channel 47. This first pressure-bearing surface D1 is bounded by the pilot valve seat surface 51. The pilot valve body 17 comprises two functional sections that are movable relative to one another and can be separated: a disk-shaped pilot valve body 17v, which abuts the pilot valve seat surface 51, and a control rod 17s. The control rod extends completely through the first control chamber 57 of the pilot valve 19 in a compression direction toward the working chamber 27 remote from the piston rod, is guided within the mainstage valve body 37, and extends into the second control chamber 58 of the pilot valve 19. In this case, the second control chamber 58 is identical to the connection chamber 65, which in turn is part of the working chamber 27 remote from the piston rod. The effective cross-sectional area of ​​the control rod 17s defines the inner edge of the first pressure-bearing surface D1. The two control chambers 57 , 58 of the pilot valve 19 are hydraulically separated by a partition wall 60 of the valve housing ring 31 , wherein the control rod 17 s is guided in an axially displaceable manner in the partition wall 60 .

[0034] The end face of the control rod 17s in the second control chamber 58 of the pilot valve 19 forms a second pressure-bearing surface D2 for the pilot valve 19 , which is only effective in the case of a throughflow originating from the working chamber 27 remote from the piston rod.

[0035] The prestressing spring 99 connects the two functional sections 17s, 17v of the pilot valve body 17 via a flange which is supported on the valve disk 37v of the main stage valve 23 and acts on the circumference of the control rod 17s.

[0036] When the damping medium flows from the working chamber 27 remote from the piston rod into the damping valve arrangement 1, it passes through the passive damping valve 35 and reaches the main stage valve 23 via the connecting chamber 65. As previously mentioned, the connecting chamber 65 forms the second control chamber 58, the pressure of which acts on the second pressure-bearing surface D2 of the pilot valve body 17 or the control rod 17s in the lifting direction.

[0037] The control volume flow flows via the connection channel 63 and the raised non-return valve disk 69 into the first control chamber 45 and subsequently into the second control chamber 55 of the main stage valve 23 or the first control chamber 57 of the pilot valve 19. In this case, the non-return valve disk 67 closes the throttle channel 47 toward the connection opening 29. The pressure in the first control chamber 57 of the pilot valve 19, in conjunction with the annular pressure-bearing surface D1, generates a further hydraulic lifting force on the pilot valve body 17, in particular the disk-shaped pilot valve body 17v.

[0038] When damping medium flows from the piston rod-side working chamber into the damping valve arrangement 1, it enters the valve housing 5 via the port opening 29 to the main stage valve 23 and reaches the first control chamber 45 of the main stage valve 23 via the throttle channel 47 and the raised non-return valve disk 67. In this case, the control volume flow also flows via the at least one port opening 53 into the second control chamber of the main stage valve or the second control chamber 57 of the pilot valve 19. Therefore, for flow from the piston rod-side working chamber 25, the pilot valve body 17 of the pilot valve 19 has only a first pressure-loaded surface D1. For flow from the piston rod-remote working chamber 27, the pilot valve 19 has a second pressure-loaded surface D2. The pilot valve 19 has a first control chamber 57 for the first pressure-loaded surface D1 and a second control chamber 58 for the second pressure-loaded surface D2. The first and second control chambers are hydraulically separated, but both the first and second pressure-loaded surfaces D1 and D2 are loaded when flow from the piston rod-remote working chamber 27 is flowing. The significant difference in the area of ​​the pressure-bearing surface, namely the area D1, results in a significantly greater lifting force acting on the pilot valve 19 when flow originates from the piston rod-side working chamber 27. This greater lifting force tends to open the pilot valve 19 to a greater extent when the damping medium pressure in the working chamber 27 distal from the piston rod is lower, whereas this does not occur at the same pressure in the piston rod-side working chamber 25. Consequently, the pressure in the first and second control chambers of the main-stage valve drops, which in turn reduces the hydraulic closing force acting on the main-stage valve body 37. The net result is that the main-stage valve 23 can open at a relatively lower damping medium pressure in the working chamber 27 distal from the piston rod than when flow originates from the piston rod-side working chamber 25.

[0039] Figure 3 Another embodiment of the present invention is shown, in which the control rod 17s does not extend beyond the main valve body 37 until it enters the interface chamber 65. Instead, the second control chamber 58 is designed as an axial channel extending from the interface chamber 65 to the end face D2 of the control rod 17s. In this example, the control chamber 58 is a stepped hole, wherein the stepped portion can be formed as a support surface for the control rod 17s. Figure 2Unlike the design of the first control chamber 57, the control rod 17s has an annular control surface 66 facing the disk-shaped pilot valve body 17v. This control surface 66, in conjunction with the pressure in the first control chamber 57, ensures a retaining force on the control rod 17s, thereby permanently connecting it to the disk-shaped pilot valve body 17v. For flow through the working chamber 25 on the piston rod side, this retaining force acts from the control surface 66. When the working chamber remote from the piston rod is compressed, the pressure acting on the second pressure-bearing surface D2 ensures this retaining force. The magnitude of the retaining force can vary greatly.

[0040] Figure 4 Another possible design of the control chambers 57, 58 and the control rod 17s is disclosed, the purpose of which is to achieve hydraulic coupling between the two functional sections 17s, 17v of the pilot valve body 17. In this variant, the pilot valve 19 has three control chambers 57, 58, 105, wherein when fluid flows from the two working chambers 25, 27 through the pilot valve 19, at least two of the control chambers are subjected to pressure in the lifting direction of the pilot valve 19. Figure 3 As in the design of the , a stepped bore is provided in the main-stage valve body 37, but this stepped bore has two steps, wherein each step forms a boundary between two adjacent control chambers. The control rod 17s has a simple stepped profile, and its first longitudinal section 17s1 has a diameter that is smaller than the diameter of the first control chamber 57.

[0041] A first longitudinal section 17 s 1 of the control rod 17 s extends into a third control chamber 105 , which adjoins the first control chamber 57 toward the second control chamber 58 .

[0042] The third control chamber 105 has a diameter that matches the diameter of the first longitudinal section 17s1 of the control rod 17s. In any stroke position of the control rod 17s, the first longitudinal section 17s1 overlaps the third control chamber 105, so that the wall of the third control chamber 105 forms a guide for the control rod 17s. The diameter of the second longitudinal section 17s2 of the control rod 17s is equal to the diameter of the third control chamber 105, and the control rod extends within the second working chamber 58 and the third working chamber 105.

[0043] The third control chamber 105 is provided with a separate connection opening 54 to the control chamber 45 of the main stage valve 23. The diameter of this connection opening 54 can be selected to be significantly smaller than the diameter of the connection opening 53 between the first control chamber 57 of the pilot valve 19 and the control chamber 45 of the main stage valve 23, for example.

[0044] When fluid flows from the piston rod-side working chamber 25 through the pilot valve 19 and into the control chamber 45 via the throttle passage 47, a control volume flow is supplied to the first and third control chambers 57 and 105, exerting a lifting force on the disc-shaped pilot valve body 17v. In this process, an annular pressure-bearing surface D1 acts in the first control chamber, and a similarly annular pressure-bearing surface D3 acts in the third control chamber. Surface D3 is determined by the diameter of the third control chamber 105, which is smaller than the diameter D1 of the first control chamber. The diameter D2 of the control rod 17s in the third control chamber 105 is equal to the diameter in the second control chamber 58, which is spatially adjacent to the third control chamber 105. Therefore, the dimensions of the third pressure-bearing surface D3 are determined by the diameter of the third control chamber 105 and the diameter of the first longitudinal section 17s1 of the control rod 17s.

[0045] For flow through the connecting chamber 65 or the working chamber 27 remote from the piston rod, the surface D2 on the control rod is directly acted upon. A portion of the control volume flow flows via the connecting channel 63 into the control chamber 45 and subsequently into the first control chamber 57 and the third control chamber 105. As a result, a total of three control chambers 57, 58, and 105 are in operation, the sum of their lifting forces being greater than the lifting force when fluid flows from the working chamber 25 on the piston rod side into the pilot valve 19. In this case, only the pressure forces from the first control chamber 57 and the third control chamber 105 of the pilot valve 19 are effective.

[0046] according to Figure 5 The design of FIG. 1 illustrates a variation of the present invention, in which the two functional sections 17s and 17v of the pilot valve body 17 are movable relative to each other, at least in the longitudinal direction. An elastic coupling element 62 is positioned between the two functional sections 17s and 17v. This coupling element is axially preloaded against the disc-shaped pilot valve body 17v by, for example, a tensioning spring 64 located within the second control chamber 58. The axial compression of the coupling element 62 determines the cross-sectional area of ​​the contact surface on the disc-shaped pilot valve body 17v. As described in conjunction with the previous figures, the effective pressure-bearing surface D1 within the first control chamber 57 is determined by the inner diameter of the pilot valve seat surface 51 minus the contact area of ​​the coupling element 62 on the disc-shaped pilot valve body 17v. Therefore, the radial extent of the first pressure-bearing surface D1 is determined by the relative axial position of the two functional sections 17s and 17v of the pilot valve body 17.

[0047] The control rod 17s has a stepped profile in the first control chamber 57 of the pilot valve 19, which has an annular control surface 66, which is loaded by the pressure in the first control chamber 57 of the pilot valve 19 and causes the control rod 17s to move toward the second control chamber 58 of the pilot valve 19 against the force of the tensioning spring 64.

[0048] The lifting stroke of the pilot valve body 17 from the pilot valve seat surface 51 determines the throttle cross section, which in turn determines the pressure levels in the first control chamber 45 and the second control chamber 55 of the main-stage valve. The pressures in the two control chambers 45 and 55 multiplied by the axial pressure-bearing area on the main-stage valve body yield an effective closing force acting on the main-stage valve body 37. Given a predetermined operating motion of the shock absorber 3, this effective closing force determines the damping force of the shock absorber 3.

[0049] Regardless of the design of the pilot valve, its control chamber, and the control rod, in all damping valve device variants, the damping medium displaced by the pilot valve 19 enters the pilot valve's return chamber 71, located between the bottom 43B of the valve housing ring 31 and the actuator 11. This return chamber is connected to a check valve assembly 73 comprising a check valve ring 75, which is equipped with at least one check valve disk 77 and 79 on either side. The check valve ring 75 is a separate and replaceable component from the valve housing ring 31. The check valve disks 77 and 79, combined with the check valve ring 75, form two check valves 81 and 83, which control the control volume flow from the pilot valve 19 into the two working chambers 25 and 27 of the working cylinder 9. The damping valve housing 5 is provided with at least one connecting opening 85, which in this example is radial, in the direction of flow from the check valve assembly 73 toward the piston rod-side working chamber 25. In order to connect the pilot valve 19 to the working chamber 27 remote from the piston rod, the valve housing ring 31 has a channel system 87 leading to the connection chamber 65. When fluid flows from one of the two working chambers 25, 27 into the non-return valve assembly 73, the non-return valve 81, 83, through which the flow flows directly, i.e., bypassing the pilot valve 19, is closed.

[0050] The non-return valve ring 75 is centered on the valve housing ring 31 via its central through-opening 89 and has an annular groove 91 in the direction of the return chamber 71, which in turn comprises an axial connection opening 93 to the channel system 87 in the valve housing ring 31. The annular groove 91 is radially delimited by two annular support surfaces 95, 97 for the non-return valve disk 77. The inner support surface 97 is interrupted by at least one radial channel 99 which connects the annular groove 91 to a connection channel 101 located radially inside. The connection channel 101 connects the return chamber 71 of the pilot valve 19 to the connection opening 93. Figure 7 )

[0051] The lifting movement of the check valve disc 79 for the channel system 87 in the valve housing ring 31 is limited by the valve housing ring 31. The cover ring 103 is used for the lifting movement of the check valve disc 77 on the top surface of the check valve ring 75, and the cover ring also axially fixes the check valve ring 75 in the damping valve housing 5.

[0052] When the flow into the working chamber 27 due to the compression away from the piston rod is Figures 5 to 7 In the damping valve arrangement 1 shown, the damping medium passes through the passive damping valve 35 and, in the connection chamber 65, ensures that the main-stage valve body 37 is pressurized within the pressure-bearing surface defined by the main-stage valve seat surface 39. The control volume flows via the connection channel 63 to the second control chamber 58 of the pilot valve 19. At least one radial channel 72 connects the second control chamber 58 of the pilot valve 19 to the first control chamber 45 of the main-stage valve 23. The check valve 70, formed, for example, by a slightly preloaded O-ring on the valve pin 49 of the main-stage valve body 37, is open in this case. The control volume flows further via the at least one connection opening 53 into the first annular control chamber 57 of the pilot valve 19. Consequently, the first pressure-bearing surface D1 on the pilot valve body 17 and the second pressure-bearing surface D2 on the control rod 17s are loaded in the lifting direction of the pilot valve 19.

[0053] The pressure in the two control chambers 45 , 55 also exerts a hydraulic closing force on the main stage valve body 37 . The control volume flows via the pilot valve 19 and the non-return valve disk 77 lifted from the non-return valve ring 75 through the connecting opening 85 into the piston rod-side working chamber 27 .

[0054] Damping medium acting on the non-return valve 83 via the channel system 87 in the valve housing ring 31 closes the non-return valve 83. The non-return valve 68 of the main stage valve body 37 is also closed when flow passes through the damping valve arrangement 1.

[0055] When fluid flows from the piston rod-side working chamber 25 into the damping valve arrangement 1, the displaced damping medium collects on the annular surface of the main-stage valve body 37, which is located radially outward from the main-stage valve seat surface 39 of the main-stage valve 23 and extends within the circumferential surface 43A of the valve housing ring 31. This displacement force also generates a lifting force on the main-stage valve body 37. The first control chamber 45 of the main-stage valve 23 is also hydraulically pressurized in parallel via the first throttle channel 47, resulting in a pressure increase in the second control chamber 55 of the main-stage valve 23. This, together with the pressure increase in the first control chamber 45, generates a closing force on the main-stage valve body 37.

[0056] The pressure in the control chamber 45 closes the check valve 70 leading to the second control chamber 58 of the pilot valve 19. The control volume flow in the first control chamber 57 of the pilot valve 19 also exerts a lifting force on the disk-shaped pilot valve body 17v, but only on the annular first pressure-bearing surface D1. As a result, the first control chamber 57 of the pilot valve 19 is also hydraulically separated from the second control chamber 58 of the pilot valve 19. A force is exerted on the control rod 17s by the pressure-loaded control surface 66 in the first control chamber 57 of the pilot valve 19, overcoming the force of the tensioning spring 64. Above a certain pressure level in the first control chamber 57 of the pilot valve 19, the control rod 17s moves toward the second control chamber 58 of the pilot valve 19, thereby reducing the compression of the elastic coupling element 62 relative to the disk-shaped pilot valve body 17v and increasing the cross-sectional area of ​​the pressure-bearing surface D1. This increase in area on the pilot valve body 17v and the resulting increase in force can be used to open the pilot valve 19 to a greater extent as the trend increases. If it is not desired that the size of the first pressure-bearing surface D1 change with pressure, the control rod 17s can be fixedly connected to the disc-shaped pilot valve body 17v and a control rod without the control surface 66 can be used.

[0057] The control volume flow flowing through the pilot valve 19 into the return chamber 71 then likewise reaches the connection channel 101, enters the annular groove 91 via the at least one radial channel 99, and can then flow out via the connection opening 93 and in conjunction with the channel system 87 into the connection chamber 65 and subsequently further out through the passive damping valve 33 into the working chamber 27 remote from the piston rod. In this case, due to the reverse throughflow originating from the working chamber 25 on the piston rod side, the check valve 81 closes toward the working chamber 25 on the piston rod side, thus achieving a rectification of the control volume flow through the pilot valve 19 by using a total of four check valves 68, 70, 81, 83.

[0058] List of reference numerals:

[0059] 1 Adjustable damping valve device

[0060] 3 shock absorbers

[0061] 5 Damping valve housing

[0062] 7 Piston rod

[0063] 9 working cylinders

[0064] 11 Actuator

[0065] 13 Excitation coil

[0066] 15 Armature

[0067] 17 Pilot valve body

[0068] 17s control stem of pilot valve body

[0069] 17v disc-shaped pilot valve body

[0070] 19 Pilot valve

[0071] 21 Return spring

[0072] 23 Main stage valve

[0073] 25 Working chamber on the piston rod side

[0074] 27 Working chamber away from the piston rod

[0075] 29 radial interface channels

[0076] 31 Valve housing ring

[0077] 33 Passive Damping Valve

[0078] 35 Passive Damping Valve

[0079] 36 pistons

[0080] 37 Main stage valve body

[0081] 37V main stage valve body disc

[0082] 37A Main stage valve body closure

[0083] 37B Main stage valve body separating piston

[0084] 39 Main stage valve seat surface

[0085] 41 valve ring

[0086] 43 Stepped opening of valve housing ring

[0087] 43A Side surface of stepped opening

[0088] 43B stepped opening bottom

[0089] 45 First control chamber

[0090] 47 First throttle channel

[0091] 49 valve pin

[0092] 51 Pilot valve seat surface

[0093] 53 interface opening

[0094] 55 Second control chamber of the main stage valve

[0095] 57 First control chamber of the pilot valve

[0096] 58 Second control chamber of the pilot valve

[0097] 60 partition wall

[0098] 61 Second control chamber

[0099] 62 coupling elements

[0100] 63 interface channels

[0101] 64 tension spring

[0102] 65 Interface chamber

[0103] 66 Control surfaces on the joystick

[0104] 67 Check valve disc

[0105] 68 Check valve

[0106] 69 Check valve disc

[0107] 70 Check valve

[0108] 71 Reflow Chamber

[0109] 72 radial channels

[0110] 73 Check valve assembly

[0111] 75 Check valve ring

[0112] 77 Check valve disc

[0113] 79 Check valve disc

[0114] 81 Check valve

[0115] 83 Check valve

[0116] 85 connection opening

[0117] 87-channel system

[0118] 89 through opening

[0119] 91 Annular groove

[0120] 93 interface opening

[0121] 95 support surface

[0122] 97 Support surface

[0123] 99 Pre-tension spring

[0124] 101 interface channel

[0125] 103 Cover Ring

[0126] 105 Third control chamber

[0127] D1 First pressure-bearing surface

[0128] D2 Second pressure surface

[0129] D3 The third pressure-bearing surface.

Claims

1. An adjustable damping valve arrangement (1) for a shock absorber (3), comprising a damping valve housing (5), in which a pilot valve (19) for hydraulically controlling a main stage valve (23) is arranged, wherein: The damping valve housing (5) is hydraulically connected to the working chamber (25) on the piston rod side and the working chamber (27) away from the piston rod of the working cylinder (9) of the shock absorber (3), wherein the damping valve device (1) has a check valve assembly (73), which is used to rectify the control volume flow from the working chambers (25, 27) of the working cylinder (9) to the pilot valve (19), characterized in that the pilot valve body (17) of the pilot valve (19) has a first pressure-bearing surface D1 for the flow from the working chamber (25) on the piston rod side and a second pressure-bearing surface D2 for the flow from the working chamber (27) away from the piston rod, wherein the pilot valve (19) has a first control chamber (57) for the first pressure-bearing surface D1 and a second control chamber (58) for the second pressure-bearing surface D2, the first control chamber being hydraulically separated from the second control chamber.

2. The adjustable damping valve device (1) according to claim 1, characterized in that: For a throughflow originating from one of the two working chambers (25, 27), the first pressure-bearing surface D1 and the second pressure-bearing surface D2 are loaded, and for a throughflow originating from the other of the two working chambers (25, 27), only the first pressure-bearing surface D1 is loaded.

3. The adjustable damping valve device (1) according to claim 1 or 2, characterized in that: The pilot valve body (17) has two functional sections (17v, 17s) that are movable relative to each other, and the two functional sections jointly define a first pressure-bearing surface D1 on the pilot valve body (17) in the radial direction.

4. The adjustable damping valve device (1) according to claim 3, characterized in that: One of the functional sections is formed by a control rod (17s) having a control surface (66) which is acted upon by the pressure in the first control chamber (57).

5. The adjustable damping valve arrangement (1) according to at least one of claims 3 or 4, characterized in that The control rod (17s) has a second pressure-bearing surface D2 with respect to the pilot valve (19), which is acted upon by the pressure in a second control chamber (58) of the pilot valve (19).

6. The adjustable damping valve arrangement (1) according to at least one of claims 1 to 5, characterized in that The radial extent of the first pressure surface D1 is determined by the relative axial positions of the two functional sections (17s, 17v) to one another.

7. The adjustable damping valve arrangement (1) according to at least one of claims 1 to 6, characterized in that One of the functional sections (17s) is guided in an axially displaceable manner in the main stage valve body (37).

8. The adjustable damping valve device (1) according to claim 7, characterized in that: The functional section (17s) capable of axially moving within the main stage valve body (37) axially penetrates the main stage valve body (37) in the compression direction toward one of the working chambers (27), and has a surface D2 that is loaded depending on the pressure generated in the working chamber (27).

9. The adjustable damping valve arrangement (1) according to at least one of claims 6 to 8, characterized in that A prestressing spring (99) connects the two functional sections (17s, 17v) of the pilot valve body (17) to one another.

10. The adjustable damping valve arrangement (1) according to at least one of claims 1 to 9, characterized in that The pilot valve (19) has three control chambers (57, 58, 105), wherein, for a flow direction from the working chambers (25, 27) through the pilot valve (19), at least two control chambers are pressurized in the lifting direction of the pilot valve (19).

11. The adjustable damping valve device (1) according to claim 10, characterized in that: The control chamber (45) for the main stage valve body (37) is connected to the two control chambers (57, 58) of the pilot valve (19).

12. The adjustable damping valve arrangement (1) according to at least one of claims 1 to 4, characterized in that The first control chamber (45) of the main-stage valve (23) and the second control chamber (58) of the pilot valve (19) are separated by a check valve (70), which prevents flow from the first control chamber (45) of the main-stage valve (23) toward the second control chamber (58) of the pilot valve (19).

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