CN116888381A - Damping valve device for shock absorber - Google Patents
Damping valve device for shock absorber Download PDFInfo
- Publication number
- CN116888381A CN116888381A CN202280014858.6A CN202280014858A CN116888381A CN 116888381 A CN116888381 A CN 116888381A CN 202280014858 A CN202280014858 A CN 202280014858A CN 116888381 A CN116888381 A CN 116888381A
- Authority
- CN
- China
- Prior art keywords
- damping
- valve device
- leg
- damping valve
- valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000013016 damping Methods 0.000 title claims abstract description 75
- 239000006096 absorbing agent Substances 0.000 title claims abstract description 15
- 230000035939 shock Effects 0.000 title claims abstract description 15
- 239000000463 material Substances 0.000 claims description 8
- 230000001419 dependent effect Effects 0.000 abstract description 2
- 230000008878 coupling Effects 0.000 description 4
- 238000010168 coupling process Methods 0.000 description 4
- 238000005859 coupling reaction Methods 0.000 description 4
- 230000005284 excitation Effects 0.000 description 4
- 230000000694 effects Effects 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 3
- 229910000831 Steel Inorganic materials 0.000 description 2
- 238000000418 atomic force spectrum Methods 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 229920001971 elastomer Polymers 0.000 description 2
- 239000000806 elastomer Substances 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000007769 metal material Substances 0.000 description 1
- 230000036316 preload Effects 0.000 description 1
- 230000036632 reaction speed Effects 0.000 description 1
- 238000007493 shaping process Methods 0.000 description 1
- 239000011343 solid material Substances 0.000 description 1
- 239000004575 stone Substances 0.000 description 1
Classifications
-
- 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
-
- 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
- F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
- F16F9/3484—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body characterised by features of the annular discs per se, singularly or in combination
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fluid-Damping Devices (AREA)
Abstract
Damping valve device (1) for a shock absorber (3), comprising a valve element (35) of variable diameter, which occupies a throttle position by a radial closing movement in the direction of a flow guiding surface (39) starting from the flow guiding position as a function of the flow velocity of a damping medium in a throttle point (37), wherein the valve element (35) comprises at least two legs (63, 65) which are mounted so as to be movable about at least one rotational bearing (67) and whose inertia (M, M) is dependent on a desired damping force characteristic (F 1 +F 5 )。
Description
Technical Field
The present invention relates to a damping valve arrangement for a shock absorber according to the preamble of claim 1.
Background
Patent document DE 10 2016 210 790 A1 discloses a damping valve device having a ring element of variable diameter which performs a radial closing movement in accordance with the flow velocity inside a throttle section, thereby changing the throttle section of the throttle section.
The annular element has transverse slits and is resilient in the radial direction. The stop ring determines the maximum expansion of the annular element and additionally also brings about a return movement of the annular element in the direction of its starting position, at which the maximum flow cross section of the throttle is also reached.
In such damping valve devices, the response characteristics of the annular element to changing flow conditions largely determine the mass of the damping valve device. The reaction speed and the size of the smallest throttle section play an important role here.
Patent document DE 10 2019 215 558 A1 proposes a ring element having at least two legs connected by a hinge. The expanding movement of the ring element is generated by the swinging movement of the legs.
Disclosure of Invention
The aim of the invention is to improve such a damping valve device in terms of functional quality.
This object is achieved in that the valve element comprises at least two legs which are supported in a manner movable about at least one rotational support and whose inertia depends on the desired damping force characteristic line.
Series tests have shown that frequency-dependent operating characteristics of the damping valve arrangement can be achieved in a meaningful way by determining the magnitude of the inertia of the valve element. Damping valve devices having lower valve element inertia also tend to react at higher frequencies and smaller travel paths of the shock absorber at constant flow rates. On the other hand, the damping force peaks of the damping valve device can be damped by the large inertia of the valve element.
In particular, if it is desired to use standardized components so that no change in flow cross section is necessary, the material of at least one leg of the valve element is advantageously selected according to the desired damping force characteristic line.
One measure for changing the inertia consists in designing the cross-sectional geometry of at least one leg according to a defined inertia. For example, a solid material may be used in the region furthest from the hinge of the valve element, and the material strength may be reduced in other regions.
For this purpose, it can also be provided that at least one leg is designed as a hollow profile.
In general, it makes sense to use a damping valve device if the valve movement is limited and continuous in order to prevent pressure peaks that can be identified as noise. If at least two legs have different inertias, then a specific excitation of the shock absorber will also react differently, which in turn causes a series of work movements which in turn causes a continuous and never abrupt damping force change.
Optionally, at least one leg may have at least one region for connection with additional mass. The inertia of the valve element can be adjusted by the additional mass.
For a simple construction of the valve element, the additional mass is axially fixed by at least one groove side of the annular groove accommodating the valve element. The annular groove thus locks at least one additional mass in the valve element.
It may also be provided that the pivotable leg comprises a leg section and a hinge section which are dimensioned according to a defined inertia. At this point, the hinge section may be matched to the support function and may be coupled to the leg section at the hinge section for adapting to the desired inertia of the valve element.
Drawings
The invention is further explained with reference to the following description of the drawings. Wherein:
fig. 1 shows a sectional view of a shock absorber in the region of a damping valve arrangement;
FIG. 2 shows a top view of the valve element according to FIG. 1;
FIG. 3 shows an alternative to the valve element of FIG. 2;
FIG. 4 shows a top view of a valve element with additional mass;
FIG. 5 shows a cross-sectional view of the valve device according to FIG. 4; and
fig. 6 shows damping force characteristic lines of the damping valve device.
Detailed Description
Fig. 1 shows a damping valve arrangement 1 for a shock absorber 3 of any type of construction, which is only partially shown. The damping valve device 1 comprises a first damping valve 5 having a damping valve body configured as a piston 7 fastened to a piston rod 9.
The damping valve body 7 divides the cylinder 11 of the shock absorber into a working chamber 13 on the piston rod side and a working chamber 15 remote from the piston rod, both working chambers being filled with damping medium. Through channels 17, 19 for the respective flow directions are formed in the damping valve body 7 on different pitch circles. The design of the through channels 17, 19 is merely exemplary. The outlet side of the through-channels 17, 19 is at least partially covered by at least one valve disk 21, 23.
In addition, the shock absorber has a pull stop 25 which, starting from a defined displacement movement of the piston rod 9, rests against a cylinder-side stop surface, for example a cylinder-side stop surface of the piston rod guide 27.
The pull-off stop 25 comprises a pull-off stop disk as a valve carrier 29 which is directly fixed to the piston rod by means of a form-fitting connection. On the upper side of the valve carrier 29, for example, an annular elastomer element 31 is placed, which is held by a slight radial preload even during the oscillating movement of the piston rod 9. Starting from the stop point at the stop surface, the elastomeric element 31 acts as an additional supporting spring.
The valve carrier 29 has a circumferential annular groove 27 in which a variable-diameter valve element 35 is guided. The valve element 35 has elasticity in the radial direction and forms a valve body for the throttle point 37 as part of the damping valve device 1. The annular element 35 forms the throttle point 31 together with the inner wall of the cylinder 11, wherein the inner wall 39 is a flow guide surface. In principle, the invention can also be implemented in a valve carrier disk independent of the pull stop.
On the outside, the valve element carries a return spring 41, which is in the form of a snap ring, for example.
When the piston rod speed is in the first operating range, for example less than 1m/s, the throttle point 37 is fully opened. At this time, damping force is generated only by the through passages 17, 19 in combination with the valve discs 21, 23. When flowing toward the valve discs 21, 23, the valve discs 21, 23 lift from their valve seat surfaces 47, 49. The lifting movement is correspondingly limited by the support discs 51, 53.
In a second operating range of the piston rod speed, which is greater than the limit speed of the first operating range, i.e. greater than 1m/s, as shown by way of example, the valve element 35 is brought into a throttle state and a closing movement is carried out in this case in the direction of the flow guide surface 39. Due to the high flow velocity of the damping medium in the throttle point 37 formed as an annular gap, a negative pressure is formed, which causes the valve element 35 to expand radially. However, in order to never cause the choke 37 to block, the defined minimum flow cross section is maintained by a mechanical stop of the return spring 41 or the valve carrier 29. The expansion movement of the valve element is supported by the pressure chamber 71 and the coupling openings, for example, the coupling openings 75, 77 to the working chamber 13, which can be seen in detail in fig. 3, whereby the dynamics of the damping valve device 1 are significantly improved and therefore the inertia of the valve element 35 has an influence on the damping force characteristics.
Fig. 2 shows a top view of the valve element 35 on the basis of the cross section of the shock absorber 3 according to fig. 1. The illustration of the valve carrier 29, the return spring 41 and the piston rod 9 is omitted for clarity. It can be seen that the valve element 35 has a lateral gap 55 that reduces the pressure required for the radial expansion movement of the valve element 35. Valve element 35 is shown in the flow-passing position at a minimum flow rate. Thus, the maximum flow cross section 57 is currently the case. The through-flow cross section 57 is defined by the inner wall 39 of the cylinder 11 and the outer circumferential surface 45 of the annular element 35.
Fig. 2 furthermore shows that the ring element 35 has at least two legs 63, 65 which are supported in a pivotable manner about a rotary support 67. In this embodiment, the leg portions 63, 65 overlap in the circumferential direction, and the rotation support portion 67 is implemented in the overlapping region. The two legs 63, 65 likewise overlap in the region of the transverse gap 55 in order to minimize disadvantageous leakage cross sections. Depending on the design of the rotary support, the valve carrier 29 can have two receiving openings 73 for receiving the support pins 69. The receiving opening in the valve carrier 29 can be configured, for example, as a simple through-hole (see fig. 1). In principle, however, different designs of the rotary support are likewise possible.
When the throttle point is activated, i.e. when a correspondingly large flow speed is present in the throttle section 57, the two legs 63, 65 of the valve element execute a radial pivoting movement about the rotary support 67 in the direction of the inner wall of the cylinder 11.
The principle of the swinging movement of the legs 63, 65 is exploited in such a way that its inertia depends on the desired damping force characteristic line. Thus, the legs are selected according to the desired damping force profile.
In the simplest variant, the shape of the legs is determined as a function of the radial installation space of the damping valve device 1, and the material of at least one of the legs 63, 65 of the valve element 35 is defined as a function of the desired damping force characteristic line. For example, a series of valve elements comprising plastic, aluminum or steel may be determined. Each variant of the valve element 35 changes the damping force characteristic of the damping valve device under otherwise identical frame conditions. It is also possible to provide at least two legs 63 with different material combinations, for example one leg 63 comprising plastic and the other leg 65 comprising steel, in order to achieve different qualities of the legs 63, 65 with the same shaping. In turn, an asymmetrical closing behavior of the damping valve device 1 can be provided, so that no excessive damping force increases occur. The same effect can be achieved if the two legs 63, 65 have different inertias because they are composed of the same material but have different shapes.
Another embodiment of the leg may be that the leg has leg sections 63a, 65a and hinge sections 63a, 65b that are sized for a defined inertia. The hinge sections 63a, 65b have relatively little effect on the operating characteristics of the damping valve arrangement. Thus, for example, standardized hinge sections 63b, 65b can be used, which are optimized for the rotary support 67. With this hinge section, leg sections 63a, 65a can be used which are optimized in particular for inertia and which also act significantly more strongly on the operating characteristics of damping valve device 1 due to the distance from rotary support 67.
Fig. 3 shows the damping valve device 1 as a separate component of the shock absorber 3. It is to be noted that the cross-sectional geometry of at least one leg 63, 65 may be designed for a defined inertia. In addition to the legs 63, 65 being made of a compact material, at least one leg 63, 65 may also be constructed of a hollow profile. The hollow profile is only shown by way of example as a tube. C-shaped profiles whose dome points in the direction of the flow-guiding surface 39, fig. 1, are also conceivable. Open hollow profiles, such as the exemplary C-profile, can also be combined with the tube profile. Finally, the decisive factor in achieving the desired damping force profile is the consumption that can be put into effect for the desired result. It can also be seen in this illustration that the swivel support 67 can also be constructed by a simple ball connection between the two legs 63, 65.
Fig. 4 and 5 show a variant of the valve element 35 of the damping valve device 1, in which variant at least one leg 63, 65 has at least one region 79 for connection to an additional mass 81. The region 79 may be formed, for example, by a blind hole opening. Arrangements on the edge side, for example in the region of the inner circumferential surfaces of the legs 63, 65, are also conceivable and expedient. The provision of the receptacle with a blind hole opening offers the advantage that the additional mass 81 does not fall off during assembly. There are preferably a plurality of receptacles, all of which are located outside of the outer peripheral surface 45, so that the use of the receptacles does not affect the basic damping force characteristics of the damping valve device 1. The larger the distance the additional mass 81 is arranged with respect to the rotary support 67, the greater the influence of the additional mass 81 on the operating characteristics of the valve element 35. For this purpose, it is expedient if the leg is made of a relatively light material, for example plastic, and the additional mass 81 is made of a metallic material. In order to retain the additional mass 81 in the receptacle for a long time, the additional mass 81 is axially fixed by at least one groove flank 85 of the annular groove 87 of the receiving valve element 35.
Fig. 6 shows the influence of the inertia of the valve element 35 on the damping force characteristic line of the damping valve device 1. The thin solid line depicts the damping force characteristic line FS of the damping valve 5 at the piston, for example. The wide solid line represents the combination of the damper valve 5 and the damper valve arrangement 1. The two solid lines show the damping force limits of the shock absorber 3. In the illustration, it is assumed that the stroke path of the shock absorber 3 is constant and the frequency of excitation is constant so that the influence can be more clearly shown.
The damping force characteristic line drawn as a broken line represents a high inertia M of the valve element, and the dash-dot line represents a relatively low inertia M. It is clearly seen that a valve element with low inertia already causes a higher damping force level when the flow velocity in the throttle position 37 is relatively small. Thus, a greater inertia causes a later reaction of the damping valve device 1 with the same boundary conditions. By virtue of this influence of the valve element, the chassis can be equipped for maximum comfort with a damping valve device having a valve element with a large inertia M, since in this case, for example, a high-frequency excitation of the stone road surface does not lead to an increase in damping force.
In a particularly sporty design of the damping valve device 1, a valve element 35 with a low inertia m is used, which reacts to small and high-frequency excitations and allows the damping force to rise. The adjustment range can be implemented in otherwise standardized damping valve arrangements.
List of reference numerals
1. Damping valve device
3. Vibration damper
5. First damping valve
7. Damping valve body
9. Piston rod
11. Cylinder body
13. Working chamber on piston rod side
15. Working chamber far away from piston rod
17. Through channel
19. Through channel
21. Valve disc
23. Valve disc
25. Traction stop
27. Piston rod guide
29. Valve carrier
31. Elastomer element
33. Groove(s)
35. Annular element
37. Throttle position
39. Inner wall
41. Reset elastic piece
45. Peripheral surface
47. Valve seat surface
49. Valve seat surface
51. Supporting disk
53. Supporting disk
55. Transverse gap
57. Through-flow cross section
59. Section bar
61. Throttle section
63. Leg portion
63a leg section
63b hinge section
65. Leg portion
65a leg section
65b hinge section
67. Rotation support part
69. Support bolt
71. Pressure chamber
73. Accommodating opening
75. Coupling opening
77. Coupling opening
79 for connection to additional mass
81. Additional mass
83. An inner peripheral surface
85. Groove side
87. An annular groove.
Claims (8)
1. Damping valve device (1) for a shock absorber (3), comprising a valve element (35) of variable diameter, which occupies a throttle position by a radial closing movement in the direction of a flow guiding surface (39) starting from the throttle position as a function of the flow rate of a damping medium in the throttle position (37), characterized in that the valve element (35) comprises at least two legs (63, 65) which are supported in a manner movable about at least one rotational support (67) and whose inertias (M, M) depend on a desired damping force characteristic line (f1+f+5).
2. Damping valve arrangement according to claim 1, characterized in that the material of at least one leg (63, 65) of the valve element depends on the desired damping force characteristic line.
3. Damping valve device according to claim 1 or 2, characterized in that the cross-sectional geometry of the at least one leg (63, 65) is designed according to a defined inertia.
4. A damping valve device according to claim 3, characterized in that the at least one leg (63, 65) is embodied as a hollow profile.
5. Damping valve device according to at least one of claims 1 to 4, characterized in that the at least two legs (63, 65) have different inertias (M, M).
6. Damping valve device according to at least one of claims 1 to 5, characterized in that at least one leg (63, 65) has at least one region (79) for connection with an additional mass (81).
7. Damping valve device according to claim 6, characterized in that the additional mass (81) is axially fixed by at least one groove flank (85) of an annular groove (87) accommodating the valve element (35).
8. Damping valve device according to at least one of claims 1 to 7, characterized in that the leg (63, 65) comprises a leg section (63 a, 65 a) and a hinge section (63 b, 65 b), which leg section is dimensioned according to a defined inertia (M, M).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE102021201427.5 | 2021-02-16 | ||
| DE102021201427.5A DE102021201427A1 (en) | 2021-02-16 | 2021-02-16 | Damping valve device for a vibration damper |
| PCT/EP2022/053591 WO2022175228A1 (en) | 2021-02-16 | 2022-02-15 | Damping valve device for a vibration damper |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN116888381A true CN116888381A (en) | 2023-10-13 |
Family
ID=80684033
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202280014858.6A Pending CN116888381A (en) | 2021-02-16 | 2022-02-15 | Damping valve device for shock absorber |
Country Status (3)
| Country | Link |
|---|---|
| CN (1) | CN116888381A (en) |
| DE (1) | DE102021201427A1 (en) |
| WO (1) | WO2022175228A1 (en) |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AU1571999A (en) * | 1997-12-16 | 1999-07-05 | Colebrand Limited | Shock transmission unit |
| US6102170A (en) * | 1998-05-07 | 2000-08-15 | Tenneco Automotive Inc. | Passive anti-roll system |
| DE102016210790A1 (en) | 2016-06-16 | 2017-12-21 | Zf Friedrichshafen Ag | Damping valve device with progressive damping force characteristic |
| DE102019215562A1 (en) | 2019-10-10 | 2021-04-15 | Zf Friedrichshafen Ag | Throttle point for a vibration damper |
| DE102019215558A1 (en) | 2019-10-10 | 2021-04-15 | Zf Friedrichshafen Ag | Throttle point for a vibration damper |
| DE102019215555A1 (en) | 2019-10-10 | 2021-04-15 | Zf Friedrichshafen Ag | Throttle point for a vibration damper |
| DE102019215559A1 (en) | 2019-10-10 | 2021-04-15 | Zf Friedrichshafen Ag | Throttle point for a vibration damper |
-
2021
- 2021-02-16 DE DE102021201427.5A patent/DE102021201427A1/en active Pending
-
2022
- 2022-02-15 WO PCT/EP2022/053591 patent/WO2022175228A1/en active Application Filing
- 2022-02-15 CN CN202280014858.6A patent/CN116888381A/en active Pending
Also Published As
| Publication number | Publication date |
|---|---|
| DE102021201427A1 (en) | 2022-08-18 |
| WO2022175228A1 (en) | 2022-08-25 |
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