CN114941677A - Damping valve device for shock absorber - Google Patents
Damping valve device for shock absorber Download PDFInfo
- Publication number
- CN114941677A CN114941677A CN202210134100.8A CN202210134100A CN114941677A CN 114941677 A CN114941677 A CN 114941677A CN 202210134100 A CN202210134100 A CN 202210134100A CN 114941677 A CN114941677 A CN 114941677A
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- Prior art keywords
- piston rod
- valve
- valve device
- damping
- cylinder
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- 238000013016 damping Methods 0.000 title claims abstract description 69
- 239000006096 absorbing agent Substances 0.000 title claims abstract description 12
- 230000035939 shock Effects 0.000 title claims abstract description 12
- 230000006870 function Effects 0.000 description 11
- 230000001419 dependent effect Effects 0.000 description 3
- 230000007704 transition Effects 0.000 description 3
- 241000239290 Araneae Species 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 238000002788 crimping Methods 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 230000006835 compression Effects 0.000 description 1
- 238000007906 compression Methods 0.000 description 1
- 230000007423 decrease Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000008571 general function Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000000750 progressive effect Effects 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/36—Special sealings, including sealings or guides for piston-rods
- F16F9/369—Sealings for elements other than pistons or piston rods, e.g. valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
- F16F9/3405—Throttling passages in or on piston body, e.g. slots
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
- F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
- F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
- F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
- F16F9/185—Bitubular units
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/3207—Constructional features
- F16F9/3221—Constructional features of piston rods
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/34—Special valve constructions; Shape or construction of throttling passages
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/36—Special sealings, including sealings or guides for piston-rods
- F16F9/362—Combination of sealing and guide arrangements for piston rods
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/48—Arrangements for providing different damping effects at different parts of the stroke
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
- F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
- F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
- F16F9/5126—Piston, or piston-like valve elements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2222/00—Special physical effects, e.g. nature of damping effects
- F16F2222/12—Fluid damping
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F2224/00—Materials; Material properties
- F16F2224/04—Fluids
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fluid-Damping Devices (AREA)
Abstract
The invention relates to a damping valve device for a shock absorber having an axially movable piston rod in a cylinder filled with a damping medium, wherein the damping medium is displaced through the damping valve device as a function of the piston rod movement, wherein a valve element of variable radial diameter is deflected in a valve seat towards a flow guide surface, wherein the flow guide surface is formed by an outer lateral surface of the piston rod.
Description
Technical Field
The present invention relates to a damping valve device for a shock absorber according to the preamble of claim 1.
Background
DE102016210790a1 discloses a damping valve device which is essentially formed by a variable-diameter valve body, a valve seat and a flow guide surface. It describes various variants of valve seats and guide surfaces which together form a damping valve device with progressive damping force characteristics.
All variants have in common that: the valve body widens radially outwards, for example towards the inner wall of the cylinder barrel, the piston skirt or the side of the base valve body.
According to the exemplary embodiment shown in fig. 4, the damping valve device can also be designed with a valve seat which is arranged in a stationary manner in the cylinder of the shock absorber.
Disclosure of Invention
The object of the invention is to show further embodiment variants for such a damping valve device.
This object is achieved in that the guide surface is formed by an outer lateral surface of the piston rod.
The outer side of the piston rod is the most valuable component inside a conventional shock absorber in terms of dimensional accuracy and surface quality. The function of the damper valve arrangement is benefited by this.
In one embodiment, the valve seat is arranged in a stationary manner in the cylinder barrel. The entire radial installation space between the side of the piston rod and the inner wall of the cylinder is available for the damping valve device.
In order to optimize the assembly effort of the damping valve device, the valve seat is formed by a piston rod guide of the cylinder. After the piston rod guide is installed, the valve seat is also fastened in the shock absorber.
In a further embodiment, the piston rod guide has a piston rod seal which seals an annular gap between the piston rod guide and a side face of the piston rod, wherein a working chamber of the vibration damper on the side close to the piston rod has a flow channel which opens into a further working chamber and which extends hydraulically parallel to the annular gap. The damping medium displaced by the damping valve device therefore does not have to flow into the compensation chamber via the annular gap toward the piston rod seal as a function of the leakage oil volume. The flow channel may be used for this purpose.
Alternatively, the piston rod can have a functional section with a guide surface which, depending on the stroke position of the piston rod inside the cylinder barrel, projects into a through-opening radially defined by the valve element and thus functionally uses the damping valve device. The functional section may be formed, for example, by an end-side piston rod pin, which projects into the valve seat. With this design, a speed-dependent function of the damping valve device as a function of the stroke position can be achieved. Alternatively, the piston rod can also have a radial constriction which does not generate a damping force when it is in register with the valve seat. However, a guide surface is also provided on the piston rod outside this constriction of the piston rod.
Alternatively, the valve seat is arranged on the piston rod. If necessary, the annular gap between the valve seat and the inner wall of the cylinder can be closed by means of a seal or at least reduced in cross section.
In a further development, the damping valve device has a first valve element of variable diameter on the inner diameter of the valve seat and a second valve element of variable diameter at a region radially further outward relative thereto toward the second flow guide surface. A better satisfactory damping valve device can be achieved with two separate valve elements.
In the simplest embodiment, the operating principle of the damping valve device is based on a speed-dependent pressure reduction inside the throttle point formed by the flow guide surface and the valve element. In an expanded embodiment, the valve seat has at least one pressure chamber which is connected to the groove for the valve element, wherein the pressure chamber is hydraulically connected to at least one working chamber of the cylinder via at least one inflow opening. The adjusting movement of the valve element can be additionally influenced by the pressure from the pressure chamber.
In a first variant, the first valve element and the second valve element are connected to a common pressure chamber. This embodiment is advantageous in particular in the case of small radial installation spaces.
Alternatively, the first valve element and the second valve element are connected to hydraulically separate pressure chambers in order to be able to apply different pressures to the two valve elements.
Drawings
The invention is explained in detail in the following description of the figures.
Wherein:
fig. 1 shows a damping valve device in the region of a piston rod guide;
fig. 2 shows the damping valve arrangement according to fig. 1 with a stroke-dependent function;
fig. 3 and 4 show the damping valve arrangement according to fig. 1 on the piston rod;
fig. 5 to 8 show a damping valve device with two valve elements.
Detailed Description
Fig. 1 shows a section through a vibration damper 1 with a cylinder 3 in which a piston rod 5 with a piston 7 performs an axial stroke movement. The piston 7 divides the cylinder 3 filled with damping medium into a piston rod-side working chamber 9 and a working chamber 11 remote from the piston rod. The two working chambers 9, 11 are hydraulically connected via damping valves 13, 15, which perform a stroke movement as a function of the pressure level at their valve disks 17, 19. The precise design of the damping valves 13, 15 is subject to the present invention.
The cylinder 3 is closed at the end by a rod guide 21 connected to a rod seal 23. An outer reservoir 25 surrounds the cylinder 3 and defines, together with the cylinder 3, a compensation chamber 27 which is only partially filled with damping medium for the damping medium volume displaced by the retracted and extended piston rod 5.
Between the outer lateral surface 29 of the piston rod 5 and the guide surface 31 of the through-opening 33 of the piston rod guide 21 there is a defined, very small annular gap which fills the oil sump 35 of the piston rod guide 21 with leakage oil from the piston rod-side working chamber 9. The through opening 33 may also be formed by a separate bearing bushing located inside the piston rod guide 21. The leakage oil volume ensures lubrication of the piston rod 5 and thus a reduction of friction. An overflow channel 37 is present between the oil sump 35 and the compensation chamber 27.
In addition to the damping valves 15, 17 in the piston 7, the vibration damper 1 has a damping valve device 39 with a valve seat 41 and a valve element 43 with a radially variable diameter. Valve element 43 forms together with guide surface 29 a throttle point 45. The higher the flow velocity inside the throttle point 45, the lower the pressure level inside the throttle point 45. Thereby deforming the valve element 43 toward the flow surface. In the case of the damping valve device 39 according to fig. 1, the flow guide surface of the damping valve device 39 is formed by the outer circumferential side 29 of the piston rod 5. The piston rod 5 thus forms part of the damping valve device 39, in particular of the throttle point 45. For a resilient valve element, for example made of plastic or a slotted metal ring, the valve element 43 narrows uniformly in diameter towards the flow guide surface 29. However, it is also possible for the valve element 43 to be composed of a plurality of individual elements forming a ring, so that the individual elements produce a radial movement or a pivoting movement about a pivot bearing point. The pivot bearing point can, for example, connect two individual elements to one another. Such an embodiment is known, for example, from the earlier document DE102019215558a 1.
Furthermore, the valve seat 41 is arranged in a stationary manner in the cylinder 3. Fig. 1 shows two embodiments of a damping valve device 39. In the left half a valve seat 41 is shown, which is independent with respect to the piston rod guide 21. The valve seat 41 does not have to bear directly against the piston rod guide 21. The fixation of the valve seat 41 inside the cylinder is simplified by direct contact. At least one crimping element 47 in the cylinder 3 ensures that the valve seat 41 is secured on both sides.
In the right half of fig. 1, the valve seat is formed by a piston rod guide 21 of the cylinder 3.
Common to both embodiments of the damping valve device 39 is that the piston-rod-side working chamber 9 of the shock absorber 1 has a flow channel 49 which opens into the other working chamber and which extends hydraulically parallel to the annular gap on the piston-rod guide 21. The further working chamber is formed in this embodiment by a compensation chamber 27 of the shock absorber 1. For this purpose, a transition opening 51 is formed in the cylinder 3, which coincides with the flow channel 49. In principle, the other working chamber can also be connected, for example, to the working chamber 11 remote from the piston rod.
The valve seat 41 has an annular groove with a diameter at the bottom 53 of the annular groove that is larger than the outer diameter of the valve element 43. The valve element is, if necessary, biased radially outward by a restoring spring 54 toward the annular groove bottom 53, but does not rest against the annular groove bottom 53. Between the annular groove bottom 53 and the valve element 43, a pressure chamber 55 is thus present, which has an inflow opening 57 from the piston-rod-side working chamber 9. The inflow opening 57 can be formed by an additional opening in the groove side wall 59 of the valve seat 41 or via a radial gap between the valve element 43 and the groove side wall 59 of the valve seat 41.
The pressure chamber 55 is connected to the compensation chamber 27 via an outflow opening 61. The outflow opening 61 can open directly into the compensation chamber 27 or be connected to the flow channel 49.
Fig. 1 shows the vibration damper 1 in a stationary state. The return spring 54 keeps the valve element 43 at a distance from the guide surface 29 of the piston rod 5. At the throttle point 45, a cross section of maximum size is present. During compression of the piston-rod-side working chamber 9, the damping medium displaces the piston 7 via the damping valve 15. In the event of a defined piston rod extension speed being exceeded, the pressure inside the throttle point 45 decreases, but the pressure in the pressure chamber 55 is increased via the inflow opening, so that an additional radial force acts on the valve element 43, which reduces the cross section of the throttle point 45 against the force of the restoring spring 54. Thereby significantly increasing the damping force level of the damping valve device 39.
Fig. 1 also shows a third variant in which the damping valve device 39 is fastened in the cylinder 3 at a distance from the piston rod guide 21. The design of the damping valve device 39 corresponds, for example, to the functional design of the damping valve device 39 at the piston rod guide 21. In order to control the damping force characteristic of the damping valve device 39, the piston rod 5 has a cross-sectional contour 63, for example a longitudinal groove or a constriction, in order to enlarge the outlet cross section of the throttle point 45 over a certain travel range of the piston rod 5. By such expansion of the throttle point 45, the initial operating point (Einsatzpunkte) of the damping valve device 39 can be determined according to the stroke position of the piston rod 5. In principle, the damping valve device 39 operates as a function of the flow velocity inside the throttle point and thus as a function of the movement of the piston rod 5. However, an and logic (Und-Verknun. upfang) with the stroke position of the piston rod 5 still exists.
The embodiment of the invention according to fig. 2 is based on a damping valve device 39 according to fig. 1. The construction and function of the valve element 43 are identical. The difference is that the piston rod 5 has a functional section 65 with a guide surface 29 which, depending on the stroke position of the piston rod 5 inside the cylinder 3, projects into a through-opening 67 radially delimited by the valve element 43, so that the damping valve device 39 is functionally used. The functional section is formed by a piston rod pin 65. In contrast to fig. 1, the damping valve device 39 is fixed in position relative to the cylinder 3 in the working chamber 11 remote from the piston rod, in this case also on the cylinder 3.
During the stroke movement, in which the piston rod pin 65 is located outside the damping valve device 39, only the damping valve 15 in the piston 7 and the foot valve 69 at the transition between the working chamber 11 and the compensation chamber 27 remote from the piston rod are active. As soon as the piston rod pin 65 with its outer guide surface 29 passes through the through-opening 67 of the valve seat 41, the damping valve device 39 can be activated. The application then additionally depends on the retraction speed of the piston rod 5.
Fig. 3 to 8 show an embodiment in which the valve seat 41 of the damping valve device 39 is arranged on the piston rod 5. The valve seat 41, the valve element 43 and the return spring 54 correspond to the construction and function according to fig. 1. The difference is that the valve seat 41 according to fig. 3 and 4 has a cylinder seal 71 which seals the annular gap between the valve seat 41 and the inner wall of the cylinder 3. The valve seat is held, for example, by two star-shaped discs 73 connected to two bearing discs 75 and two retaining rings 77 on the piston rod 5. The spider has radial recesses, as is known from spider springs. In principle, an alternative fastening technique is of course also conceivable. The flow path along deflector surface 29 on the inner diameter of valve seat 41 should be more readily understood in conjunction with this illustration.
When the piston rod moves, the damping medium can escape from the compressed piston-rod-side working chamber 9 through the throttle point 45 and then through the valve 15 in the piston 7 into the working chamber 11 remote from the piston rod. However, if the speed of the piston rod 5 also increases here beyond a defined limit, the inner diameter of the valve element 43 and thus also the cross section of the throttle point 45 is reduced. This radial constriction of the throttle point 45 is supported by the effect of the pressure chamber 55 according to the embodiment shown in fig. 1.
Fig. 5 to 8 relate to an embodiment variant of the damping valve device 39, which has a first valve element 43A of variable diameter on the inner diameter of the valve seat 41 and a second valve element 43B of variable diameter at a radially outer region thereof in the direction of the second flow guide surface 79. The seal used in fig. 3 and 4 is therefore replaced by an additional valve element 43B. The inner wall of the cylinder thus forms a second deflector surface 79. The second valve element 43B also has a restoring spring 81, which however generates a radially inwardly directed restoring force.
Just like the valve element 43A for the throttle point 45A interacting with the piston rod 5, the throttle point 45B also has a pressure chamber with the inner wall of the cylinder 3 as a flow surface 79. The first and second valve elements 43A, 43B are connected to a common pressure chamber 55.
The two throttle points 45A, 45B which are already present can be used in succession by designing the throttle cross section in its initial position in combination with the return springs 54, 81, so that a damping force characteristic of the shock absorber 1 which is stepped in the direction of the steps is produced. Here, the ratio of the surfaces to which pressure is applied to the valve elements 43A, 43B also plays an important role. The pressure-loaded surface, i.e. the radially inner and outer side surfaces at the second valve element 43B, is significantly larger than the comparable surface at the inner first valve element 43A.
Fig. 7 and 8 show an alternative damper valve device 39 with two damper valve elements 43A, 43B, the first and second valve elements 43A, 43B being connected to hydraulically separate pressure chambers 55A, 55B. Thus, separate inflow openings 57A, 57B and outflow openings 61A, 61B are also present, by means of whose cross-section the respective pressure level in the pressure chambers 55A, 55B can be adjusted as a function of the piston rod speed. The initial point of action and the closing characteristic of the two valve elements 43A, 43B can be controlled independently of one another with different cross-sectional dimensions. The general function of this embodiment corresponds to that described with respect to fig. 5 and 6.
List of reference numerals:
1 vibration damper
3 cylinder barrel
5 piston rod
7 piston
9 working chamber at one side of piston rod
11 working chamber far away from piston rod
13 damping valve
15 damping valve
17 valve disk
19 valve disk
21 piston rod guide
23 piston rod seal
25 container
27 compensating chamber
29 side/flow guide surface
31 guide surface
33 through opening
35 oil pool
37 overflow channel
39 damper valve device
41 valve seat
43 valve element
45 throttle point
47 crimping element
49 flow channel
51 transition opening
53 annular groove bottom
54 return spring
55 pressure chamber
57 inflow opening
59 groove side wall
61 outflow opening
63 contour
65 functional section
67 through opening
69 bottom valve
71 cylinder barrel seal
73 star-shaped disc
75 supporting disc
77 retainer ring
79 second flow guide surface
81 return spring
Claims (10)
1. A damping valve device (39) for a shock absorber (1) having an axially movable piston rod (5) in a cylinder (3) filled with a damping medium, wherein the damping medium is displaced through the damping valve device (39) as a function of the piston rod movement, wherein a valve element (43) of variable radial diameter is deflected in a valve seat (41) towards a flow guide surface (29), characterized in that the flow guide surface (29) is formed by an outer side of the piston rod (5).
2. The damping valve device according to claim 1, characterized in that the valve seats (41, 21) are arranged in a stationary manner in the cylinder barrel (3).
3. A damper valve device according to claim 2, characterized in that the valve seat (41) is formed by a piston rod guide (21) of the cylinder (3).
4. A damping valve device according to claim 3, characterized in that the piston rod guide (21) has a piston rod seal (23) which seals an annular gap between the piston rod guide (21) and a side face (29) of the piston rod, wherein the working chamber (9) of the shock absorber on the side close to the piston rod has a flow channel (49) which opens into the other working chamber (27), said flow channel running hydraulically parallel to the annular gap.
5. The damper valve device according to claim 2, characterized in that the piston rod (5) has a functional section (65) with a guide surface (29) which, depending on the stroke position of the piston rod (5) inside the cylinder (3), projects into a through-opening (67) radially defined by the valve element (43) and thus functionally uses the damper valve device (39).
6. The damper valve device according to claim 1, characterized in that the valve seat (41) is arranged on the piston rod (5).
7. A damper valve device according to claim 6, characterized in that the damper valve device (39) has a first valve element (43A) of variable diameter on the inner diameter of the valve seat (41) and a second valve element (43B) of variable diameter at a radially further outer region relative thereto towards the second guide surface (79).
8. Damping valve device according to at least one of claims 1 to 7, characterized in that the valve seat (41) has at least one pressure chamber (55) which is connected to a groove for the valve element (43, 43A, 43B), wherein the pressure chamber (55) is hydraulically connected to at least one working chamber (9, 11) of the cylinder (3) via at least one inflow opening (57, 57A, 57B).
9. The damping valve device according to claim 8, characterized in that the first and second valve elements (43A, 43B) are connected at a common pressure chamber (55).
10. The damper valve arrangement according to claim 8, characterized in that the first and second valve elements (43A, 43B) are connected at hydraulically separated pressure chambers (55A, 55B).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
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DE102021201420.8 | 2021-02-16 | ||
DE102021201420.8A DE102021201420B4 (en) | 2021-02-16 | 2021-02-16 | Damping valve device for a vibration damper |
Publications (1)
Publication Number | Publication Date |
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CN114941677A true CN114941677A (en) | 2022-08-26 |
Family
ID=82610738
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
CN202210134100.8A Pending CN114941677A (en) | 2021-02-16 | 2022-02-14 | Damping valve device for shock absorber |
Country Status (2)
Country | Link |
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CN (1) | CN114941677A (en) |
DE (1) | DE102021201420B4 (en) |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4328319A1 (en) | 1993-08-23 | 1995-03-02 | Hemscheidt Maschf Hermann | Cylinder-piston unit for a hydropneumatic suspension |
DE102008042634B4 (en) | 2008-10-07 | 2010-07-08 | Zf Friedrichshafen Ag | Vibration damper with amplitude-selective damping force |
DE102016210790A1 (en) | 2016-06-16 | 2017-12-21 | Zf Friedrichshafen Ag | Damping valve device with progressive damping force characteristic |
DE102019215558A1 (en) | 2019-10-10 | 2021-04-15 | Zf Friedrichshafen Ag | Throttle point for a vibration damper |
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2021
- 2021-02-16 DE DE102021201420.8A patent/DE102021201420B4/en active Active
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