阅读说明：本技术 用于振动阻尼器的阻尼阀 (Damping valve for vibration damper ) 是由 A·克内泽维奇 J·罗塞勒 于 2018-10-25 设计创作，主要内容包括：一种用于振动阻尼器的阻尼阀,该阻尼阀包括具有至少一个通过通道(13；15)的阻尼阀体(7),该通过通道由至少一个阀盘(23)至少部分地覆盖,其中阀盘(23)由平面弹簧(27)预加载到阀座面(29)上,其中弹簧(27)的接触区域具有弹性体涂覆物(41)。(A damping valve for a vibration damper, comprising a damping valve body (7) with at least one through-passage (13; 15) which is at least partially covered by at least one valve disk (23), wherein the valve disk (23) is preloaded onto a valve seat surface (29) by a planar spring (27), wherein the contact area of the spring (27) has an elastomer coating (41).)

1. A damping valve for a vibration damper, comprising a damping valve body (7) with at least one through-passage (13; 15) which is at least partially covered by at least one valve disk (23), wherein the valve disk (23) is preloaded onto a valve seat surface (29) by a planar spring (27), characterized in that the contact area of the spring (27) has an elastomer coating (41).

2. The damper valve according to claim 1, characterized in that the spring (27) has an elastomer coating (41) on both sides.

3. The damper valve according to claim 2, characterized in that the elastomer coating (41) on the first cover face (43) differs from the elastomer coating (41) of the second cover face (45) in terms of spring rate.

4. The damper valve according to claim 1, characterized in that the planar spring (27) is embodied as a star spring with a plurality of spring arms (47).

5. The damper valve according to claim 4, characterized in that the spring rate of the elastomer coating (41) of one spring arm (47) of the star spring (27) differs from the spring rate of the elastomer coating (41) of the other spring arm (47).

6. The damper valve according to claim 4, characterized in that the side edges (49) of at least one spring arm (47) have an elastomer coating (41).

7. The damper valve according to claim 4, characterized in that the spring arm (47) has a recess (51) for receiving an elastomer material.

Technical Field

The present invention relates to a damping valve for a vibration damper according to the preamble of patent claim 1.

Background

DE 102010039196 a1 describes a damping valve for a vibration damper, in which a star spring is attached as a possible design of a planar spring to a tilting disk, which influences the spring behavior of the star spring. In the case of tilting disks with a larger diameter, the star spring is strengthened. In addition to the star springs, disk springs are usually used, which can likewise be regarded as flat springs.

In DE 102015206022 a1, a further method is used to influence the lifting behavior of the valve disk. An elastomeric element held by a rigid support disc is used. The valve disc itself is made of spring steel into a simple metal disc.

In principle, a damping valve in which the valve disk is relatively weakly preloaded for high driving comfort tends to vibrate itself. To avoid such self-vibrations, the at least one valve disc is preloaded more than may be necessary for a comfortable but still reliable chassis setting.

Disclosure of Invention

The aim of the invention is to minimize this comfort loss range of the damping valve.

This object is achieved by: the contact area of the spring has an elastomer coating.

The elastomer coating by means of the flat spring performs a resonant displacement in which the lifting movement of the valve disk can be achieved without disturbing noise when the vibration damper is excited at low frequencies.

In terms of a simple and replacement-safe assembly, the spring can have an elastomer coating on both sides. However, the two-sided elastomer coating can also be used: the elastomeric coating on the first cover surface of the damper differs from the elastomeric coating of the second cover surface in terms of spring rate. Such a coating arrangement can, for example, influence the lifting behavior of the valve disk by means of a spring, which then, after a defined spring travel, with its second cover face, bears against a second spring or support disk and subsequently the second elastomer coating determines a further deformation path and thus the lifting behavior.

In principle, it is possible for a flat spring to provide a disk spring known per se. Preferably, the planar spring is embodied as a star spring with a plurality of spring arms.

Not only can the spring stiffness be varied in a manner related to the cover surface of the spring, but also: the spring rate of the elastomer coating of one spring arm of the star spring is different from the spring rate of the elastomer coating of the other spring arm. A support region of the spring with a greater support force is then realized in comparison with a support region with a smaller support force. The valve disk is therefore always lifted in a defined manner at the circumferential region, with minimal supporting forces being present. Undesirable noise can likewise be avoided thereby.

The side edges of at least one spring arm also have an elastomer coating in terms of durability of the elastomer coating.

Additionally, to better secure the elastomer coating, the spring arm may have a recess for receiving the elastomer material.

Detailed Description

Fig. 1 shows a detail of a vibration damper 1 with a cylinder 3 filled with damping medium, in which a piston rod 5 is guided in an axially movable manner. The piston rod 5 carries a piston 7 as a damping valve body, which divides the cylinder 3 into a piston-rod-side working space 9 and a working space 11 remote from the piston rod.

The piston 7 has a passage channel 13 for the separate flow direction of the damping medium as a result of the piston rod movement; 15. during the compression of the piston-rod-side working space 9, the outlet opening through the channel 13 is at least partially covered by a rigid valve disk 17 connected to a helical compression spring 19. So-called pre-open discs 21 are usually applied. Such a valve structure may however only be considered as exemplary.

The outlet openings for flow through the through passages in the opposite direction are at least partially covered by the valve disc 23. In this example, the valve disk is elastic and has a clamping region 25 next to the inner diameter. Alternatively, a rigid valve disk can also be used, which is raised over the entire surface of the damping valve body or of the cover of the piston 7.

The valve disk 23 is preloaded against the valve seat surface 29 by a flat spring in the form of a disk spring 27 of a construction known per se. A rigid support disk 31 arranged above the disk spring 27 delimits the deformation path of the disk spring 27 during the lifting movement of the valve disk 23. For this purpose, the support disk 31 has a contour in the direction of the star spring 27, which contour extends radially outward from the clamping surface 33 with the outer inclined edge 35. The inclined edge 35 adjoins a bevel 37 which transitions into a contact surface 39 for the disk spring 27. The passage 15 in the piston 7 together with the valve disk and the disk spring 27 forms a damping valve 28 for one direction of movement of the piston 7.

Furthermore, the region of the disk spring 27 which is in contact with the valve disk 23 has an elastomer coating which is in this case applied to the first cover surface 43 and the second cover surface 45. As shown in a comparison of the cross-sectional area on the left side of the disk spring 27 with the cross-sectional area on the right side, the radial positioning of the elastomer coating on the circumferential area can be changed. It is likewise possible to design the profile or, for example, the coating height non-uniformly over the circumference.

As partially shown in detail according to fig. 2, the elastomer coating 41 on the first cover side 43 can differ from the elastomer coating 41 of the second cover side 45 with respect to the spring rate.

During the lifting movement of the valve disk 23, the elastomer coating 41 and the disk spring 27 act like two springs 41 in series; 27 function as well. However, in contrast to the lamellar disk spring, a metallic contact between the valve disk 23 and the disk spring 27 is avoided. The same applies to the contact between the belleville springs 27 and the support disc 31. Depending on the spring characteristic, either the elastomer coating 41 is initially axially preloaded more strongly or the metal core of the disk spring 27 is initially deformed. A soft initial setting of the characteristic curve 27 of the disk spring can be achieved without the valve disk 23 having to be brought into resonance.

When the disk spring 27 strikes with its top or second cover surface 45 against the support disk 31, then again no impact noise can occur and the supporting force does not start suddenly, but increases depending on the geometry of the elastomer coating 41.

Fig. 3 will show that the planar spring is not limited to a disk spring, but can also be embodied as a star spring 27 with a plurality of spring arms 47.

Smaller closing forces can also be achieved by means of the star spring 27, and by dividing the spring volume into a plurality of spring arms 47, the spring arms 47 can have different geometries and deflect independently of one another. Furthermore, the following possibilities exist: the spring rate of the elastomer coating 41 of one spring arm 47 of the star spring 27 is different from the spring rate of the elastomer coating 41 of the other spring arm 47. The difference may also be in material selection, for example. Other parameters have been exemplarily enumerated in connection with the disc spring.

Fig. 4 will show that the side edges 49 of at least one spring arm 47 may also have an elastomer coating 41. The load of the elastomer coating 41 in the circumferential direction can be more easily supported via the side edges 49. Additionally, the spring arm 47 can have a recess 51 for receiving an elastomer material in order to achieve a form-fitting connection with the star spring in addition to the material-fitting connection with the star spring. Such a form-fitting connection 53 is illustrated in cross section in fig. 5.

List of reference numerals

1 vibration damper

3 Cylinder body

5 piston rod

7 piston

9 working space on piston rod side

11 working space far away from piston rod

13; 15 through the channel

17 valve disk

19 helical compression spring

21 pre-opening disc

23 valve disk

25 clamping area

27 star spring

28 damping valve

29 seat surface

31 supporting disk

33 clamping surface

35 inclined edge

37 bevel

39 contact surface

41 elastomer coating

43 first cover

45 second cover surface

47 spring arm

49 side edge

51 notch

53 form-fitting connection