Damper valve and vibration damper

Abstract

The invention relates to a damper valve and a vibration damper. The invention relates to a damper valve for a vibration damper, in particular of a motor vehicle, comprising a valve body, at least one control disc arranged on the valve body and at least one rotatably mounted adjusting element, the valve body, the control disc and the adjusting element being coaxially arranged, the control disc is connected to the adjusting element for common rotation and the control disc is rotatable relative to the valve body so as to open at least one of a plurality of through-channels in the valve body for dampening or blocking flow of fluid wherein the valve body comprises a plurality of recesses having different opening areas, and wherein the control disc is rotatable relative to the valve body so as to open at least one of the plurality of through-channels in the valve body for dampening or blocking flow of fluid. The opening area is covered by at least one valve disc, and in each case, one through channel opens into one of the recesses.

Description

Technical Field

[0001] The present invention relates to a damper valve and a vibration damper.For example, a damper valve according to the preamble of a first inventive aspect is known from JP 2012 145 171A. Background Art

[0002] Precise and easy adjustment of the damping force is important, in particular in the field of sports motor vehicles. There, vibration dampers with variable damping force usually have a switchable valve device, for example, by means of which a connecting channel in a piston can be opened or closed in order to vary the damping force.

[0003] For example, JP 2012 145 171A mentioned at the beginning discloses a vibration damper with an adjustable damping force, wherein the setting is carried out via an adjustable piston valve. The piston valve has a plurality of valve discs arranged one above the other, wherein each valve disc has two integrated flexible sheet metal tongues. The sheet metal tongues of the valve discs are placed one above the other in a stepped manner. The valve discs form a disc group that can rotate together around the longitudinal axis of the piston rod. The rotation of the disc group occurs in an actuating element arranged in the piston rod and which can be rotated from the outside by an operator. During the setting of the damping force, the spring characteristics of the disc group change because the protruding length of the sheet metal tongue in the piston is lengthened or shortened. The disadvantage here is that the vibration damper for adjusting the damping force has a complex structure and is therefore very costly.

[0004] A further vibration damper with an adjustable piston valve is known, for example, from KR 2017 068 300A.

[0005] Also known from the prior art are adjustable valves for setting the damping force, in which a spring disk package prestressed by a spring is used. Due to the prestressing of the spring, different opening pressures can be set. It is known that the prestressing of the spring disk package is so high that an actuation by an operator, i.e. a manual actuation, is not possible. This leads in particular to the disadvantage that setting losses may occur, which can affect the spring prestressing. In addition, such valve units have increased overall dimensions and increased weight. Another disadvantage is that the characteristics of the characteristic curve that can be adjusted by the spring tensioning change when adjusting the coating of the spring disk. Summary of the invention

[0006] The invention is based on the object of specifying a damper valve for a vibration damper which, due to an improved structure, allows an easy and precise setting of the damping force of the vibration damper. The invention is also based on the object of specifying a vibration damper having such a damper valve.

[0007] According to the present invention, the object of the damper valve is achieved by the technical solution of the first invention. Regarding the vibration damper, the above object is achieved by the technical solution of the second invention.

[0008] In particular, the object is achieved by a damper valve for a vibration damper, in particular for a vibration damper of a motor vehicle, the damper valve having a valve body, at least one control disk arranged on the valve body and at least one rotatably mounted adjusting element, wherein the valve body, the control disk and the adjusting element are arranged coaxially. The control disk is connected to the adjusting element for common rotation and the control disk can be rotated relative to the valve body in order to open at least one through-channel of a plurality of through-channels in the valve body for the flow of damper fluid or to block the flow. The valve body comprises a plurality of recesses with different opening areas, the opening areas being covered by at least one valve disk, wherein in each case one through-channel in each case opens into one of the recesses.

[0009] The basic concept of the invention is that, due to the rotation of the control disk, a plurality of interconnections of the through-channel with the recess in the valve body can be achieved. Since the recess comprises opening areas with different sizes, the total opening area of ​​the valve body for opening the valve disc can be increased or reduced by rotating the control disk. Since the valve disc covers the opening area of ​​the recess, a change in the total opening area results in an adjustment of the size of the pressurized area of ​​the valve disc. Due to the damper valve according to the invention, the damping force can thus be easily and precisely set in order to achieve a softer or harder damping of the vibration damper as required.

[0010] Another advantage of the invention is that it is possible to actuate the control disk by the operator, i.e. by hand, since, in contrast to the solutions known from the prior art, the actuation does not take place counter to the prestressing force of the spring, but rather the control disk is rotated via the adjusting element. Furthermore, the necessary opening force and therefore the damping force remain unaffected by any setting losses. In addition, the damper valve according to the invention can be produced with smaller overall dimensions and reduced weight.

[0011] The greater the number of through-channels opened by the control disk, the greater the number of recesses in which the pressurized damper fluid flows, so that the damping fluid comes into contact with the pressurizable area of ​​the valve disk via the opening area of ​​the recesses. In other words, the size of the total opening area increases with the number of through-channels opened by the control disk into the recesses. Due to the larger pressurized area of ​​the valve disk, the valve disk is lifted even at lower fluid pressures so that the damping fluid can pass through. In this way, soft damping or softer damping of the vibration damper is achieved.

[0012] The fewer the number of through-channels opened by the control disc, the fewer the number of recesses in which the pressurized damping fluid flows, so that the damping fluid comes into contact with the pressurizable area of ​​the valve disc via the opening area of ​​the recess. Due to the smaller pressurized area of ​​the valve disc, the valve disc is only lifted under increased fluid pressure so that the damping fluid can pass through. In this way, hard damping or harder damping of the vibration damper is achieved. Alternatively, the control disc can block all through-channels. In this state, the total opening area is equal to zero, and therefore no damping fluid can pass through the valve body. In other words, in this state, the flow of the damper fluid through the through-channels and therefore via the valve disc is completely blocked.

[0013] Preferably, the control disk can be rotated incrementally, in particular stepwise, by means of the adjusting element in order to increase or decrease the total opening area. In other words, it is advantageous when the adjustment of the damping force is performed in equal steps. For this purpose, the control disk can be rotated relative to the valve body by means of the adjusting element. In other words, the control disk can advantageously be actuated via the adjusting element. In this case, the rotation of the control disk can be performed in equal steps by means of the adjusting element. This allows a simple and precise setting, in particular a reproducible setting, of the damping force of the vibration damper.

[0014] The total opening area corresponds to the sum of all opening areas of those recesses which are fluidically connected to the associated through-channel, in particular the through-channel opened by the control disk.The pressurized area of ​​the valve disk preferably corresponds to the opening area of ​​the recesses arranged opposite in each case.

[0015] The total opening area can be formed, for example, by the opening area of ​​a single recess. Alternatively, the total opening area can include opening areas of multiple, in particular at least two recesses. Preferably, the total opening area includes opening areas of at least three recesses, particularly preferably at least four recesses.

[0016] The opening area is to be understood as that area which spans the recess at its fluid outlet side. The opening area is covered by the valve disc. This means that the opening area faces the valve disc. Thus, the opening area forms an extended opening of the recess spanned by the valve disc.

[0017] The recess is preferably formed in a pocket-like manner in the valve body. In other words, the recess is preferably a cutout which is open toward the valve disk via an opening area on one side thereof and into which one of the through-channels in each case opens on the other side.

[0018] Within the meaning of the invention, the adjustment of the total opening area includes both a complete closure of the through-channels, in which case no damper fluid passes through the through-channels, and a complete opening of the through-channels, in which case the damping fluid passes through all through-channels unhindered. Furthermore, the control disk is designed to occupy any desired intermediate position between the complete opening or the complete closure of the through-channels. For this purpose, the control disk can be rotated about its common rotation axis by means of the adjusting element.

[0019] It is particularly advantageous if the damper valve allows a bypass flow in the vibration damper to be regulated or damped. In conjunction with the vibration damper, the damper valve is preferably arranged to allow a flow of damper fluid between working spaces of the vibration damper, which are separated from one another by the working piston, bypassing the piston valve of the working piston. In other words, a bypass fluid connection can be created, by which a partial flow of the damper fluid passing through the damper valve is guided past the piston valve. This depends, for example, on the rebound phase or the pressure phase of the vibration damper.

[0020] It is also advantageous that the damper valve allows the bypass to be completely closed. This is achievable when all through-passages are blocked by the control disk and therefore the bypass flow or partial flow of the damper fluid through the damper valve is substantially equal to zero.

[0021] Preferably, the damper valve is used for a vibration damper of a motor vehicle. The damper valve is suitable for damping the rebound phase or the pressure phase of the vibration damper. Particularly preferably, the damper valve is used for a vibration damper used for racing cars, since the damper valve allows an incremental adaptation of the damping force and thus the damping can be precisely adapted to the characteristics of the race track or the driving style, etc. Often, it is necessary to carefully approach the optimal setting, which the damper valve according to the invention allows. The invention is not limited to use on vibration dampers for racing cars. Other fields of application are also possible.

[0022] Preferred embodiments of the present invention are described in detail in the dependent claims.

[0023] In a particularly preferred embodiment, the through-channel in the valve body can be selected and / or blocked by the control disk so that in at least one rotational direction of the control disk, the opening areas of the recesses are added together or subtracted from one another. This should preferably be understood to mean that a rotation of the control disk in a clockwise or counterclockwise direction in particular results in the through-channel in the valve body being opened or blocked. In this case, the factor by which the opening area varies in one rotational direction of the control disk can differ from one rotational position to the next. In this case, adding the opening areas of the recesses together advantageously results in a softer damping. Since the opening areas of the recesses are subtracted from one another, a harder damping can be set.

[0024] In a preferred embodiment, the control disk has a plurality of openings for each through-channel in the valve body, wherein, depending on the rotational position of the control disk, one or more of the through-channels are opened by an opening or the control disk blocks a through-channel. The control disk preferably forms a central switching disk with a plurality of switching openings. The control disk thus has a structure that is as simple as possible and has an increased fail-safety.

[0025] In another preferred embodiment, the openings in the control disk and / or the through-channels in the valve body are arranged on different hole circles. Particularly preferably, the control disk and the valve body comprise the same hole circle. The control disk and / or the valve body can have two hole circles or three hole circles. Particularly advantageously, the control disk and / or the valve body have four hole circles. Thus, the openings in the control disk and the through-channels in the valve body are arranged in an improved structural manner, so that a compact overall size of the damper valve can be achieved.

[0026] Preferably, the openings in the control disk and the through-channels in the valve body located on the same hole circle correspond to each other or are spaced apart from each other depending on the rotational position of the control disk. If the openings are spaced apart from the through-channels, the control disk will block the through-channels, in particular all of the through-channels.

[0027] It is also preferred that the control disk can be rotated incrementally by the adjusting element and comprises at least 4, in particular 8 or 10, preferably at least 16 rotational positions in the rotational direction in order to open and / or block the through-channel. Advantageously, the damper valve can be used for different fields of application due to the variable number of rotational positions. Particularly preferably, the control disk can be moved into 10 rotational positions or 16 rotational positions. It is also advantageous that a plurality of different rotational positions allows for improved adjustability of the damping.

[0028] In a further preferred embodiment, the number of rotational positions of the control disk corresponds to the square of the number of opening areas of the recesses in the valve body. If the valve body has, for example, four recesses with different opening areas, the control disk can be moved into 16 rotational positions. Since the preferably four recesses in the valve body have different opening areas, the total opening area can be varied in the 16 rotational positions of the control disk. In the following table, by way of example, 16 rotational positions are illustrated, in which four different opening areas can be set for forming a total opening area by blocking or opening four through-channels in the valve body. In this case, the total opening area corresponds to the pressurized area of ​​the valve disk during operation of the damper valve. The values ​​of the area are given in square millimeters (mm 2 ) is given.

[0029]

[0030]

[0031] In a preferred embodiment, the opening area of ​​at least one of the recesses is larger than the inlet area of ​​the through-channel leading to the recess. Advantageously, all through-channels have an inlet area facing the respective recess which is smaller than the opening area. Thus, the through-channels take up less space in the valve body. The larger opening area makes it easier to lift or open the valve disc.

[0032] In one embodiment, at least two of the through-channels in the valve body have inlet areas with different flow cross sections. This is advantageous because, in addition to the area effect, the smaller / larger flow cross section also utilizes the flow effect in order to actuate the valve disk.

[0033] In another preferred embodiment, at least one of the recesses or more recesses is in the form of a pocket and extends in the radial direction. At least one of the recesses or more recesses may extend in the radial direction in an annular manner. In other words, at least one of the recesses or more recesses may extend in the circumferential direction of the valve body. The recess and therefore the opening area in the valve body are designed in a space-saving manner.

[0034] Preferably, the valve body has at least one shoulder, the at least one shoulder adjoining the recess and the valve disc inserted into the at least one shoulder. Particularly preferably, the valve disc is received in the valve body, in particular arranged in an integrated manner. Thus, the damper valve is designed in a more compact manner.

[0035] The control disk is preferably preloaded against the valve body by at least one spring element, in particular a conical spring and / or a cup spring. This serves to fix the position of the control disk. As a result, the control disk is optimally placed against the valve body. Furthermore, as a result, the control disk can be placed tightly against the valve body, which increases functional reliability.

[0036] The valve disc can be pressed against the valve body by at least one spacer. Additionally or alternatively, the valve disc can be preloaded against the valve body by means of a threaded connection. The advantage of both variants is that the valve disc is pressed against the valve disc seat of the valve body and thus allows a tight abutment in the unactuated state and resets the valve disc in the actuated state, that is to say in the open state.

[0037] The damper valve preferably comprises at least one actuating member which is connected to the adjusting element for co-rotation, wherein the actuating member is accessible from the outside and preferably can be rotated by hand. This has the advantage that no overloading of the adjusting mechanism and thus no damage to the adjusting mechanism, for example due to incorrect operation of a tool, can occur. This increases the life of the adjusting mechanism. Furthermore, an easy and precise setting of the damping by hand is allowed.

[0038] The adjusting element can be in the form of an adjusting shaft extending through the valve body and the control disk, wherein the control disk is arranged on the adjusting shaft for co-rotation and the valve body is rotationally decoupled from the adjusting shaft. The damper valve can additionally have at least one retaining component, into which the valve body is at least partially inserted, in particular pressed, and through which the adjusting element extends. Particularly preferably, the retaining component forms a counter-bearing for the spacer in order to preload the valve disk against the valve body. The retaining component serves both for fixedly receiving the valve body and for rotatably mounting the adjusting shaft, and thus achieves an advantageous dual function.

[0039] Advantageously, the valve body has a plurality of return channels which pass through the valve body and are arranged in a manner distributed in the circumferential direction. Particularly preferably, the return channels are formed in a circumferential region of the valve body. The return channels can be open on one side on the valve disc side and covered on the other side by the control disc. Preferably, the control disc and / or the valve disc are designed in an elastic manner. The return channels are preferably covered flexibly by the control disc. In other words, the control disc implements a non-return function, wherein the control disc blocks the flow of the damper fluid in the damping direction and enables the flow to be opposite to the damping direction. As a result of the functional integration, the structure of the damper valve is simplified.

[0040] According to a further independent aspect, the invention relates to a vibration damper for a motor vehicle, having at least one damper valve according to the invention, wherein the damper valve is fluidically connected or can be fluidically connected to at least one working space and / or compensation space of the vibration damper in order to set the damping force.

[0041] For the advantages of the vibration damper, reference is made to the advantages explained in connection with the damper valve.Furthermore, alternatively or additionally, the vibration damper may have individual features or a combination of several features mentioned above in connection with the damper valve.

[0042] The invention is explained in more detail in the text that follows with reference to further details of the drawings.The illustrated exemplary embodiment represents an example of how a damper valve according to the invention may be constructed. BRIEF DESCRIPTION OF THE DRAWINGS

[0043] In the attached picture:

[0044] Figure 1 shows a longitudinal section through a vibration damper with two damper valves according to an exemplary embodiment of the invention;

[0045] Figure 2 Shown through the Figure 1a longitudinal cross-section of a damper valve in the damper valve;

[0046] Figure 3 Shown according to Figure 2 A plan view of a control disk of a damper valve, wherein the opening in the control disk is clearly visible;

[0047] Figures 4 to 13 Shown according to Figure 2 Plan view of a valve body of a damper valve, wherein a control disk arranged on the rear side is illustrated in different rotational positions.

[0048] In the following, the same reference numerals will be used for identical parts or identically acting parts. DETAILED DESCRIPTION

[0049] Figure 1 A vibration damper 100 with two damper valves 10 according to an exemplary embodiment of the present invention is shown, wherein the damper valves 10 are used for rebound phase damping and pressure phase damping. In addition, the vibration damper 100 may have, for example, two further damper valves not shown. Figure 1 The two damper valves 10 shown in the figure are used for rebound phase damping and pressure phase damping in the high speed range. In contrast, the other two damper valves are used for rebound phase damping and pressure phase damping in the low speed range. The vibration damper 100 is preferably used for a motor vehicle. Particularly preferably, the vibration damper 100 is used for a sports motor vehicle, in particular for a racing car or sports car. Other fields of application are also possible.

[0050] according to Figure 1 , the vibration damper 100 has a first working space 101 and a second working space 102, which are separated from each other by a working piston 103. The working spaces 101, 102 are filled with a damper fluid, in particular a hydraulic oil. In addition, there is a compensation space (not shown) for receiving and discharging at least a portion of the damper fluid corresponding to the piston rod volume. The compensation space is arranged on the outside, i.e. a compensation space is provided on the outside and can be connected to one or two damper valves 10 via a connector 104. The damper valves 10 are fluidically connected to the working spaces 101, 102, so that the first damper valve 10 damps the rebound phase and the second damper valve 10 damps the pressure phase. The two damper valves 10 are arranged on the outside of the vibration damper 10, preferably one above the other.

[0051] In the rebound phase, preferably, the bypass between the working spaces 101, 102 is opened via the damper valve 10, so that in addition to the main flow, the damper fluid also flows through the damper valve 10 via the piston valve of the working piston 103. In this process, the damper fluid flows from the first working space 101 to the second working space 102 via one of the damper valves in the damper valve 10, so that the fluid flow is damped. In this process, a portion of the damper fluid corresponding to the inserted piston rod volume flows out of the compensation space and flows into the working space 102. In this case, the rebound phase damping is achieved by the damper valve 10.

[0052] In the pressure phase, the damper fluid flows primarily from the second working space 102 into the first working space 101 via the piston valve of the working piston 103. The portion of the damper fluid corresponding to the inserted piston rod volume flows out of the second working space 102 and flows via one of the damper valves 10 into the external compensation space and is damped in the process by the damper valve 10. In this case, pressure phase damping is thus achieved by the damper valve 10.

[0053] In the following, reference will be made to Figures 2 to 13 , the structures and functions of the two damper valves 10 are described based on one of the valves 10 .

[0054] Figure 2 A longitudinal section through one of the damper valves 10 is shown. The damper valve 10 has a valve body 11, a control disk 12 arranged on the valve body 11 and an adjusting element 13 which is mounted in a rotatable manner. Furthermore, the damper valve 10 has a valve disk 16 which is likewise arranged on the valve body 11. The valve body 11, the control disk 12, the adjusting element 13 and the valve disk 16 are arranged coaxially. In other words, the valve body 11, the control disk 12, the adjusting element 13 and the valve disk 16 are located on a common axis A. The control disk 12 is connected to the adjusting element 13 for common rotation, wherein the control disk 12 is rotatable relative to the valve body 11. In other words, the control disk 12 is mounted so as to be rotatable about the axis A via the adjusting element 13. The control disk 12 is connected to the adjusting element 13 by a form fit. From Figure 2 and Figures 4 to 13 It is obvious that the control disk 12 and the regulating element 13 are coupled via a simple connection. Other types of connections are also possible. The valve body 11 and the valve disk 16 are stationary. In other words, the valve body 11 and the valve disk 16 are arranged in a non-rotatable manner.

[0055] As in Figure 2As can be seen in the figure, the valve body 11 has a first side 28, against which the control disc 12 is placed. Furthermore, the valve body 11 has a second side 29, which is the side opposite to the first side. The valve disc 16 is placed against the second side 29. On the second side 29, the valve body 11 comprises a shoulder 21, wherein the valve disc 16 is arranged in the shoulder 21. In other words, the valve disc 16 has been inserted into the valve body 11. Or in other words, the valve disc 16 is arranged in the valve body 11 in an integrated manner. The valve disc 16 will be discussed in more detail below.

[0056] also, Figure 2 It is shown that the control disc 12 is placed tightly against the first side 28 formed in a flat manner. This is achieved by the control disc 12 being preloaded against the first side 28 of the valve body 11 by the spring element 22. The spring element 22 is a conical spring in this case. Alternatively, the spring element 22 can be one or more cup springs. Other types of springs are also possible.

[0057] The spring element 22 is supported on a support element 31 which is spaced apart from the control disk 12 along the axis A. The support element 31 rests against a component 32 which is connected to the adjustment element 13 and forms a counter-support for the support element 31 .

[0058] As from Figures 4 to 13 As is evident therein, the valve body 11 comprises a plurality of through-channels 14a to 14d through the valve body 11. The through-channels 14a to 14d each form a free passage from a first side 28 to a second side 29 of the valve body 11. The through-channels 14a to 14d are in the form of holes.

[0059] Furthermore, the valve body 11 has a plurality of return channels 26 which pass through the valve body 11 and are arranged in a uniformly distributed manner in the circumferential direction. The return channels 26 connect the two side parts 28, 29 of the valve body 11. On the first side part 28, in particular on the control disk side, the return channels 26 are covered by the control disk 12. In order to ensure that the channels 26 are opened in the event of a return flow, the control disk 12 is formed in an elastic manner. Therefore, in addition to the switching function, the control disk 12 also serves as a non-return disk for the return damper fluid flow.

[0060] In addition, from Figures 4 to 13It is evident that the valve body 11 has a plurality of recesses 15a to 15d, wherein in each case one through-channel of the through-channels 14a to 14d opens into one of the recesses 15a to 15d. The recesses 15a to 15d are formed in a recessed manner in the valve body 11. In particular, the valve body 11 has four recesses 15a to 15d and four through-channels 14a to 14d. Thus, each recess 15a to 15d forms one through-channel 15a to 15d in order to allow the flow of the damper fluid.

[0061] like Figure 2 As shown in , the recesses 15a to 15d are formed in the valve body 11 in an integral manner. Specifically, the recesses 15a to 15d are formed starting from the disc support 33 of the valve body 11 in the direction of the first side 28 of the valve body 11. The recesses 15a to 15d form pockets and are open toward the valve disc 16. In other words, the recesses 15a to 15d are formed in an open manner in the direction of the second side 29 of the valve body 11. The recesses 15a to 15d extend in the radial direction and partially extend in the circumferential direction of the valve body 11. In other words, the recesses 15a to 15d are formed in an annular manner. Or, in other words, the recesses 15a to 15d form an annular recessed portion in the valve body 11. The recesses 15a to 15d are arranged continuously and in a manner spaced apart from each other in the circumferential direction. The recesses 15a to 15d are arranged in a distributed manner around the axis A.

[0062] like Figures 4 to 13 As shown in , the opening area 18 of the first recess 15a is smaller than the opening area 18 of the second recess 15b. In addition, the opening area 18 of the second recess 15b is smaller than the opening area 18 of the third recess 15c. In addition, the opening area 18 of the third recess 15c is smaller than the opening area 18 of the fourth recess 15d. The fourth recess 15d has the largest opening area 18.

[0063] exist Figure 2 As can be seen in FIG. 1 , the valve disc 16 completely spans, in particular covers, the recesses 15 a to 15 d. Figures 4 to 13 It is evident that the recesses 15a to 15d have different opening areas 18. The opening areas 18 correspond to those wide openings of the recesses 15a to 15d that face the valve disk 16. The opening area 18 is directly covered by the valve disk 16, in particular in the unactuated state.

[0064] It is also clear from the figure that each opening area 18 of the recesses 15a to 15d is larger than the inlet area 19 of the through-channels 14a to 14d leading to the recesses 15a to 15d. It is also clear that the through-channels 14a to 14d have different inlet areas 19. In other words, the through-channels 14a to 14d have different flow cross sections.

[0065] The through-channels 14a to 14d can be selected by the control disk 12. This means that the through-channels 14a to 14d can be opened or blocked by rotating the control disk 12. The through-channels 14a to 14d in the valve body 11 can be selected and / or blocked by the control disk 12 such that, for example, in a first rotational direction of the control disk 12, the opening areas 18 of the recesses 15a to 15d are added together or, for example, in a second, opposite rotational direction of the control disk 12, the opening areas of the recesses 15a to 15d are subtracted from one another.

[0066] For this purpose, the control disk 12 has a plurality of openings 17a to 17d for each through-opening 14a to 14d in the valve body 11, wherein, depending on the rotational position of the control disk 12, one or more of the through-channels 14a to 14d are opened by the openings 17a to 17d, or the through-channels 14a to 14d are blocked by the control disk 12. Figure 3 In addition, Figure 3 It is evident from the figure that the openings 17a to 17d are arranged on different hole circles L1 to L4. The through-channels 14a to 14d in the valve body 11 are also arranged on different hole circles L1 to L4.

[0067] In the following, the positions of the openings 17a to 17d in the radial direction from the inside to the outside are explained. The opening 17c in the control disk 12 for the third through-channel 14c in the valve body 11 is arranged on the first hole circle L1. The third through-channel 14c leads to the third recess 15c. The opening 17a in the control disk 12 for the first through-channel 14a in the valve body 11 is arranged on the second hole circle L2. The first through-channel 14a leads to the first recess 15a. The opening 17d in the control disk 12 for the fourth through-channel 14d in the valve body 11 is arranged on the third hole circle L3. The fourth through-channel 14d leads to the fourth recess 15d. The opening 17b in the control disk 12 for the second through-channel 14b in the valve body 11 is arranged on the fourth hole circle L4. The second through-channel 14b leads to the second recess 15b. Therefore, the through-channels 14a to 14d are also arranged on different hole circles so as to correspond to the associated openings 17a to 17d in the control disk 12. The different interconnects are discussed in detail below.

[0068] according to Figure 2 , the recesses 15a to 15d meet the shoulder 21. The disc support 33 is used to support the valve disc 16 and is arranged at the transition between the recesses 15a to 15d and the shoulder 21. The disc support 33 is a support surface for sealing support of the valve disc 16.

[0069] like Figure 2As can be seen in the figure, the valve disc 16 lies on the disc support 33. This corresponds to an unactuated state of the valve disc 16, in which no damper fluid flows through the through-channels 14a to 14d. This may be the case when all through-channels 14a to 14d are blocked by the control disc 12 or the vibration damper 100 is in a stationary state. In the unactuated state, the valve disc 16 completely covers or closes the recesses 15a to 15d.

[0070] Not illustrated is the actuated state of the valve disk 16, in which the damper fluid flows through one or more of the through-channels 14a to 14d into the recesses 15a to 15d and thereby lifts the valve disk 16 off the disk support 33. In this case, the control disk 12 is in a rotational position in which the control disk 12 opens one or more of the through-channels 14a to 14d.

[0071] The valve disk 16 is designed in an elastic manner so as to be lifted off from the disk support 33 and to return automatically. Figure 2 The valve disk 16 is shown pressed against the valve body 11 by means of the spacer 27 in a radially inner position. Starting from this position, the valve disk 16 can be deformed in a flexible, ie elastic, manner radially outwards.

[0072] according to Figure 2 , the damper valve 10 has a holding part 25 which comprises a receptacle 34 for the valve body 11. The valve body 11 is partially pressed into the receptacle 34 of the holding part 25 at the front side. The valve body 11 is thus connected to the holding part 25 for common rotation. The holding part 25 is in turn arranged in a valve housing 105 of the vibration damper 100 (see Figure 1 ). Figure 2 As can be seen in FIG, the spacer 27 is supported against the face of the holding part 25 forming the counter-support. Specifically, the spacer 27 is supported against the bottom of the receiving portion 34 of the holding part 25. The spacer 27 is a rigid element. Preferably, the spacer 27 is conical and extends around the adjustment element 13.

[0073] Due to the crimping of the valve body 11 and the retaining part 25, the spacer 27 is pressed against the bottom of the receiving portion of the retaining part 25 and thus preloads the valve disk 16 against the disk support 33 of the valve body 11. In order to fix the valve body 11 in place, the valve body 11 and the retaining part 25 have radially extending holes. In the radially extending holes, fixing means (not shown), in particular grub screws, can be introduced to establish a force-fitting and / or form-fitting connection between the valve body 11 and the retaining part 25.

[0074] from Figure 2It is also evident that the adjusting element 13 is rotatably mounted in the holding part 25. The adjusting element 13 extends through the holding part 25, wherein the adjusting element 13 is partially arranged in the holding part 25. The holding part 25 fixes the position of the adjusting element 13 in the longitudinal direction, i.e. on the axis A. The adjusting element 13 is in the form of a shaft and can therefore also be referred to as an adjusting shaft 24. The adjusting shaft 24 extends through the valve body 11 and the control disk 12, wherein the control disk 12 is arranged on the adjusting shaft 24 for co-rotation and the valve body 11 is rotationally decoupled from the adjusting shaft 24.

[0075] from Figure 1 It is evident that the damper valve 10 has an actuating member 23 connected to an adjusting shaft 24 for common rotation. The actuating member 23 is accessible from the outside and can be rotated by hand. It is evident that the actuating member 23 is a hand wheel in the form of a sleeve attached to the adjusting shaft 24.

[0076] In the following, reference is made to Figures 4 to 13 , describes different rotational positions of the control disk 12 relative to the varying total opening area or pressurized area of ​​the valve disk 16. Specifically, Figures 4 to 13 A total of 10 switching positions of the damper valve 10 are shown, wherein the control disk 12 is moved from a first rotational position (see Figure 4 ) starts to rotate counterclockwise. Figures 4 to 13 The damping can be adjusted incrementally from hard to soft. The rotational position of the control disk 12 is set in a defined rotational angle pattern. In the present case, the control disk 12 is rotated by 36° about the axis A from one rotational position to the next by the adjustment shaft 24 in each case. This allows incremental adjustment. Other angle increments are possible.

[0077] exist Figures 4 to 13 In the embodiment shown in FIG. 1 , the control disk 12 is concealed by the valve body 11. In order to better illustrate the switching positions, the valve disk 16 and all other components are concealed. Figures 4 to 13 The dashed line in is necessary in order to identify the rotational position of the covered control disk 12 .

[0078] therefore, Figure 4 A first rotational position is shown, in which the control disk 12 blocks all four through-channels 14a to 14d, so that no damper fluid can flow into the recesses 15a to 15d, and the valve disk 16 remains on the disk support 33. Thus, on the first side 28 of the valve body 11, the through-channels 14a to 14d are completely covered by the control disk 12. This corresponds to the hardest damping setting of the damper valve 10. In the first rotational position, the total opening area and therefore the pressurized area of ​​the valve disk 16 is equal to zero.

[0079] exist Figure 5In the embodiment shown in FIG. 1 , the control disk 12 has been rotated 36° counterclockwise about the axis A. Here, the control disk 12 is in a second rotational position, in which one of the first openings 17a in the control disk 12 coincides with the first through-channel 14a and thus opens the first through-channel 14a. During operation, the damper fluid flows through the first through-channel 14a into the 2 mm 2 The first recess 15a of the first opening area 18 is formed. Therefore, the pressurized area of ​​the valve disc 16 also corresponds to 2 mm 2 During operation, the damper fluid therefore flows into the first recess 15a and lifts the valve disc 16 off the disc support 33 at least at the level of the first recess 15a. This corresponds to a very stiff damping.

[0080] exist Figure 6 , the control disk 12 has been rotated 36° counterclockwise about the axis A relative to the second rotational position of the control disk 12. Here, the control disk 12 is in a third rotational position, in which one of the second openings 17b in the control disk 12 coincides with the second through-channel 14b and thus opens the second through-channel 14b. During operation, the damper fluid flows through the second through-channel 14b into the 4 mm 2 The second recess 15b of the second opening area 18 is formed. Therefore, the pressurized area of ​​the valve disc 16 also corresponds to 4 mm 2 As a result, the damping is set at a slightly softer level than in the second rotational position of the control disc 12 .

[0081] exist Figure 7 , the control disk 12 has been rotated 36° counterclockwise about the axis A relative to the third rotational position of the control disk 12. Here, the control disk 12 is in a fourth rotational position, in which one of the first openings 17a coincides with the first through-channel 14a, and one of the second openings 17b in the control disk 12 coincides with the second through-channel 14b, and thus both channels 14a, 14b are open. During operation, the damper fluid flows through the two through-channels 14a, 14b into the two recesses 15a, 15b, so that their opening areas 18 (2 mm 2 and 4mm 2 ) added together to form 6mm 2 The total opening area of ​​the valve disc 16 therefore also corresponds to a pressurized area of ​​6 mm. 2 As a result, the damping is set at a slightly softer level than in the third rotational position of the control disc 12 .

[0082] exist Figure 8, the control disk 12 has been rotated 36° counterclockwise about the axis A relative to the fourth rotational position of the control disk 12. Here, the control disk 12 is in a fifth rotational position, in which one of the third openings 17c in the control disk 12 coincides with the third through-channel 14c and thus opens the third through-channel 14c. During operation, the damper fluid flows through the third through-channel 14c into the 8 mm 2 The third recess 15c of the third opening area 18 is formed. Therefore, the pressurized area of ​​the valve disc 16 also corresponds to 8 mm 2 As a result, the damping is set at a slightly softer level than in the fourth rotational position of the control disc 12 .

[0083] exist Fig. 9 , the control disk 12 has been rotated 36° counterclockwise about the axis A relative to the fifth rotational position of the control disk 12. Here, the control disk 12 is in the sixth rotational position, in which one of the first openings 17a coincides with the first through-channel 14a, and one of the third openings 17c in the control disk 12 coincides with the third through-channel 14c, and thus both channels 14a, 14c are open. During operation, the damper fluid flows through the two through-channels 14a, 14c into the two recesses 15a, 15c, so that their opening area 18 (2 mm 2 and 8mm 2 ) are added together to form 10mm 2 The total opening area of ​​the valve disc 16 therefore also corresponds to a pressurized area of ​​10 mm. 2 As a result, the damping is set at a slightly softer level than in the fifth rotational position of the control disc 12 .

[0084] exist Fig.10 , the control disk 12 has been rotated 36° counterclockwise about the axis A relative to the sixth rotational position of the control disk 12. Here, the control disk 12 is in the seventh rotational position, in which one of the second openings 17b coincides with the second through-channel 14b and one of the third openings 17c in the control disk 12 coincides with the third through-channel 14c, and thus both channels 14b, 14c are open. During operation, the damper fluid flows through the two through-channels 14b, 14c into the two recesses 15b, 15c, so that their opening areas 18 (4 mm 2 and 8mm 2 ) add together to form 12mm 2 The total opening area of ​​the valve disc 16 therefore also corresponds to a pressurized area of ​​12 mm. 2 As a result, the damping is set at a slightly softer level than in the sixth rotational position of the control disc 12 .

[0085] exist Fig.11 , the control disk 12 has been rotated 36° counterclockwise about the axis A relative to the seventh rotational position of the control disk 12. Here, the control disk 12 is in the eighth rotational position, in which one of the first openings 17a coincides with the first through-channel 14a, and one of the fourth openings 17d in the control disk 12 coincides with the fourth through-channel 14d, and thus both channels 14a, 14d are open. During operation, the damper fluid flows through the two through-channels 14a, 14d into the two recesses 15a, 15d, so that their opening area 18 (2 mm 2 and 16mm 2 ) added together to form 18mm 2 The total opening area of ​​the valve disc 16 therefore also corresponds to a pressurized area of ​​18 mm. 2 As a result, the damping is set at a slightly softer level than in the seventh rotational position of the control disc 12 .

[0086] exist Fig.12 , the control disk 12 has been rotated 36° counterclockwise about the axis A relative to the eighth rotational position of the control disk 12. Here, the control disk 12 is in a ninth rotational position, in which one of the second openings 17b coincides with the second through-channel 14b, and one of the fourth openings 17d in the control disk 12 coincides with the fourth through-channel 14d, and thus both channels 14b, 14d are open. During operation, the damper fluid flows through the two through-channels 14b, 14d into the two recesses 15b, 15d, so that their opening areas 18 (4 mm 2 and 16mm 2 ) add together to form 20mm 2 The total opening area of ​​the valve disc 16 therefore also corresponds to a pressurized area of ​​20 mm. 2 As a result, the damping is set at a slightly softer level than in the eighth rotational position of the control disc 12 .

[0087] exist Fig.13, the control disk 12 has been rotated 36° counterclockwise about the axis A relative to the ninth rotational position of the control disk 12. Here, the control disk 12 is in the tenth rotational position, in which a first opening of the first openings 17a coincides with the first through-channel 14a, a second opening of the second openings 17b coincides with the second through-channel 14b, a third opening of the third openings 17c in the control disk 12 coincides with the third through-channel 14c, and a fourth opening of the fourth openings 17d coincides with the fourth through-channel 14d, and thus all four channels 14a to 14d are open. During operation, the damper fluid flows through the four through-channels 14a to 14d into all four recesses 15a to 15d, so that their opening areas 18 (2 mm 2 , 4mm 2 , 8mm 2 and 16mm 2 ) together to form 30mm 2 The total opening area of ​​the valve disc 16 therefore also corresponds to a pressurized area of ​​30 mm 2 As a result, the damping is set at a slightly softer level than in the ninth rotational position of the control disc 12. This rotational position of the control disc 12 produces the softest damping.

[0088] It should be noted that the number of openings in the control disk 12, the number of through-channels in the valve body 11 and the number of recesses with different opening areas are not limited to Figures 3 to 13 In different configurations, the invention can include more or fewer openings, recesses and opening areas. Thus, more or less than 10 rotational positions and thus more or less than 10 switching positions of the damper valve 10 can be provided. This allows a high degree of variability in the production and use of the damper valve 10 according to the invention.

[0089] Reference numerals list

[0090] 10 Damper valve

[0091] 11 Valve body

[0092] 12 Control Panel

[0093] 13. Regulating elements

[0094] 14a-14d Through-passage

[0095] 15a-15d recess

[0096] 16 Valve disc

[0097] 17a-17d Opening in control panel

[0098] 18 Opening area of ​​the recess

[0099] 19 Entrance area of ​​the through passage

[0100] 21 Shoulders

[0101] 22 Spring element

[0102] 23 Actuating components

[0103] 24 Adjustment axis

[0104] 25. Retaining parts

[0105] 26 Return channel

[0106] 27 Spacer

[0107] 28 First side of valve body

[0108] 29 Second side of valve body

[0109] 31 Support element

[0110] 32 Components connected to the regulating element

[0111] 33. Disc support

[0112] 34 Reception Department

[0113] 100 Vibration Damper

[0114] 101 First Workspace

[0115] 102 Second Workspace

[0116] 103 Working piston

[0117] 104 Connectors for compensating spaces

[0118] 105 valve housing

[0119] L1-L4 hole circle

[0120] A axis

Claims

1. A damper valve (10) for a vibration damper, in particular a vibration damper for a vehicle, the damper valve (10) comprising a valve body (11), at least one control disk (12) arranged on the valve body (11) and at least one rotatably mounted adjusting element (13), wherein: The valve body (11), the control disk (12) and the regulating element (13) are coaxially arranged, and wherein the control disk (12) is connected to the regulating element (13) for common rotation, and the control disk (12) is rotatable relative to the valve body (11) so as to open at least one through-channel of a plurality of through-channels (14a, 14b, 14c, 14d) in the valve body (11) for the flow of damper fluid, or to block the flow, It is characterized in that The valve body (11) comprises a plurality of recesses (15a, 15b, 15c, 15d) with different opening areas (18), which are covered by at least one valve disk (16), wherein in each case one through-channel (14a, 14b, 14c, 14d) respectively opens into one of the recesses (15a, 15b, 15c, 15d).

2. The damper valve according to claim 1, It is characterized in that The through-channels (14a, 14b, 14c, 14d) in the valve body (11) can be selected and / or blocked by the control disk (12) so that in at least one rotation direction of the control disk (12), the opening areas (18) of the recesses (15a, 15b, 15c, 15d) are added together or subtracted from each other.

3. The damper valve according to claim 1 or 2, It is characterized in that The control disk (12) has a plurality of openings (17a, 17b, 17c, 17d) for each through-channel (14a, 14b, 14c, 14d) in the valve body (11), wherein, depending on the rotational position of the control disk (12), one or more of the through-channels (14a, 14b, 14c, 14d) are opened by the openings (17a, 17b, 17c, 17d), or the control disk (12) blocks the through-channels (14a, 14b, 14c, 14d).

4. Damper valve according to any of the preceding claims, in particular according to claim 3, It is characterized in that The openings (17a, 17b, 17c, 17d) in the control disk (12) and / or the through-channels (14a, 14b, 14c, 14d) in the valve body (11) are arranged on different hole circles (L1, L2, L3, L4).

5. The damper valve according to claim 3 or 4, It is characterized in that The openings (17a, 17b, 17c, 17d) in the control disk (12) and the through-channels (14a, 14b, 14c, 14d) in the valve body (11) located on the same hole circle (L1, L2, L3, L4) correspond to each other or are spaced apart from each other depending on the rotational position of the control disk (12).

6. Damper valve according to any one of the preceding claims, It is characterized in that The control disk (12) can be rotated incrementally by the adjusting element (13) and comprises at least 4, in particular 8 or 10, preferably at least 16 rotational positions in the rotational direction in order to open and / or block the through-channel (14a, 14b, 14c, 14d).

7. Damper valve according to any one of the preceding claims, It is characterized in that At least one of the recesses (15a, 15b, 15c, 15d) has an opening area (18) that is larger than an inlet area (19) of the through-channel (14a, 14b, 14c, 14d) leading to the recess (15a, 15b, 15c, 15d).

8. Damper valve according to any one of the preceding claims, It is characterized in that At least two of the through-channels (14a, 14b, 14c, 14d) in the valve body (11) comprise inlet areas (19) having different flow cross sections.

9. Damper valve according to any one of the preceding claims, It is characterized in that At least one or more of the recesses (15a, 15b, 15c, 15d) is in the form of a pocket and extends in the radial direction.

10. Damper valve according to any one of the preceding claims, It is characterized in that At least one or more of the recesses (15a, 15b, 15c, 15d) extend in a radial direction in an annular manner.

11. Damper valve according to any one of the preceding claims, It is characterized in that The valve body (11) has at least one shoulder (21) which adjoins the recess (15a, 15b, 15c, 15d) and into which the valve disc (16) is inserted.

12. Damper valve according to any one of the preceding claims, It is characterized in that The control disk (12) is preloaded against the valve body (11) by at least one spring element (22), in particular a conical spring and / or a cup spring.

13. A damper valve according to any one of the preceding claims, It is characterized in that The valve disc (16) is pressed against the valve body (11) via at least one spacer (27).

14. Damper valve according to any one of the preceding claims, It is characterized in that At least one actuating part (23) is connected to the adjusting element (13) for joint rotation, wherein the actuating part (23) is accessible from the outside and can preferably be rotated by hand.

15. Damper valve according to any one of the preceding claims, It is characterized in that The adjusting element (13) is in the form of an adjusting shaft (24) which extends through the valve body (11) and the control disk (12), wherein the control disk (12) is arranged on the adjusting shaft (24) for co-rotation and the valve body (11) is rotationally decoupled from the adjusting shaft (24).

16. Damper valve according to any one of the preceding claims, It is characterized in that At least one holding part (25) is provided, into which the valve body (11) is at least partially inserted, wherein the adjusting element (13) extends through the holding part (25).

17. A damper valve according to any one of the preceding claims, It is characterized in that The valve body (11) has a plurality of return channels (26) which penetrate the valve body (11) and are arranged distributed in a circumferential direction.

18. The damper valve according to claim 17, It is characterized in that One side of the return channel (26) is open on the valve disk side, and the other side is covered by the control disk (12).

19. A damper valve according to any one of the preceding claims, It is characterized in that The control disk (12) and / or the valve disk (16) are designed in an elastic manner.

20. A vibration damper (100) for a motor vehicle, the vibration damper (100) having at least one damper valve (10) according to any one of the preceding claims, wherein: The damper valve (10) is fluidically connected or can be fluidically connected to at least one working volume (101, 102) and / or a compensation volume of the vibration damper (100) in order to set a damping force.

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