DE8221277U1 - Hydraulic shock absorber - Google Patents

Description

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Hydraulic shock absorber

The invention relates to a hydraulic shock absorber with one the working cylinder in two hydraulic chambers dividing working piston, with at least one axially extending in the pulling direction, the chambers together connecting hydraulic channel, as well as a hydraulic flow through the channel controlling disk valve, wherein the valve disk with a throttle passage delimiting a radially extending flow path for permanent connection of the two hydraulic chambers is provided and that the pressurized Valve surfaces on the compression and rebound side are formed by ring channels, the ring channel the rebound side towards the piston has a smaller distance than that of the compression side.

In known shock absorbers of this type (DE-PS 22 64 139) should also with a high throttling and damping effect of the throttle path passing through the piston valve a low-noise operation in the valve closing system guaranteed. For this purpose, there is another between the valve disk and the valve seat Valve disk with an axial flow path extending axially through it between the hydraulic channel and the throttle passage limiting the throttle

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Opening provided. In such a combined coil spring plate valve has the disadvantage that the valve disc, which is pressed against the valve seat, as well as all other valve disks arranged underneath can only bend in a break-proof manner, when the radial bending length is relatively large. For this reason, the valve seat diameter is radially small the rebound valve side of the piston, as it is in the usual design with small piston diameters results, such a solution is not possible.

Starting from this, it is the object of the invention to provide a vibration damper on the rebound side of a vibration damper To create coil spring plate valve, the bending length of which is dimensioned so that even in diameter small and therefore small valve seat diameters having a vibration damper piston there is sufficient resistance to breakage, so that a long service life even under extreme conditions is achieved.

To solve this problem, the invention provides that on the rebound side axially between the piston and the valve disc a rigid piston head is arranged, which together with the piston a first and a disk together with the valve forms the second valve seat, the diameter of the disk and piston head formed between the valve second valve seat has a larger diameter than that formed between the piston and piston head first valve seat.

The advantage of this design is that there is an independent flow path for the pressure stage side the vibration damper oil is present and that on

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the outer underside of the piston head a second, annular valve seat was created, which is larger in diameter than the diameter of the valve seat on the piston. In the rebound stage, a flow path is created via bores and annular channels in the piston and bores as well as the annular channel of the piston head and finally on the lifting valve disks on Piston poppet valve seat. By enlarging the outer support diameter of the valve disks in contrast to the diameter of the tension stage side The valve seat on the piston has a relatively large radial bending length in relation to the inside diameter of the cylinder of the valve disks reached. By increasing the bending length of the valve disc, the Increased break resistance, so that with an increase in the service life even under extreme conditions is to count.

According to a further essential feature it is provided that the piston plate on its outer periphery Has channels or a conical outer surface, which with the ring channels and the axial hydraulic channels work together on the compression side.

The advantage of this design is that it is independent of the piston and also of the piston head and its valve seat diameter the channels can be designed so that the grooves e.g. on the outer circumference of the piston head open up and thus clear a flow path for the vibration damper oil in the pressure stage. By such a Design, the construction is independent of the outer channels and the second or first valve seat diameter.

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In a preferred embodiment of the invention it is provided that between the outer surface of the piston and the inner wall of the cylinder one with the Piston clamped contact seal, e.g. a plastic ring, a PTFE film or the like is.

Here, the piston head can advantageously be designed so that it is used directly as a span! ement can be used for the contact seal on the piston. However, it can also be used to fix the piston foil a support pot can be used on the top of the piston.

Furthermore, there is the standardization of the individual

Components, because the piston with its compression and rebound passages can advantageously be used as a

Unit parts are produced, and the piston head

then serves as a variable component to deal with different

Flow cross-sections different damper settings to ensure.

Preferred embodiments according to the invention are shown schematically in the drawings.

It shows:

FIG. 1 shows a valve mechanism as a detail of a shock absorber;

Figure 2 shows another embodiment of a valve in principle as already shown in FIG.

The piston valve shown in FIG. 1 essentially consists of the piston 8, the piston head 1 and the valve disks 15 and 15 '. Between the valve plate 17 and the valve nut 18 is supported the valve spring 19 from. The piston 8, piston plate 1,

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Valve disks 15, 15 'and the piston nut 16 together form an axial one on the piston rod 21 Bracing chain.

Outer channels 5 are arranged in the piston 8, which are formed into annular channels 6 and 7 on the end faces of the piston open and over the grooves 4 of the piston head 1 a Flow path for the vibration damperö! form in the pressure stage, with the piston head 1 opposite side a pressure stage valve 9 is provided.

The piston 8, together with the valve disk 1, forms a first valve seat 3. The second valve seat 2. which is larger in diameter than the first valve seat 3, is through the valve disk 1 and the valve disks 15 formed. The first valve seat 3 and the second valve seat 2 are the rebound stage of the Vibration damper assigned.

On the underside of the piston head 1 is located an annular channel 1o with bores 11 which connect the annular channel 1o to the bores 12 of the piston 8. the Bores 12 of the piston 8 open into annular channels 13 and 14 in both end faces of the piston 8 in this way a flow path arises in the rebound stage via the bores 12 and the annular channels 13 and 13 14 of the piston 8 and the bores 11 and the annular channel 1o of the piston head 1 and finally via the on the second valve seat 2 lifting valve disks The upper valve disk 15 'is on the outside diameter provided with constant passages 22 for the low speed range.

On the circumferential surface of the piston 8 is a piston

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Foil 2o is provided, which is braced by the end face of the piston head 1 and a shoulder of the piston 8 will.

In Figure 2, a piston valve is shown, which corresponds in principle to that in Figure 1 with the difference, that the piston foil 2o by a support pot 24 on the top of the piston 8 and by a shoulder 25 of the piston itself is tensioned. Otherwise, this exemplary embodiment corresponds to that in FIG. 1. The conical outer surface 26 of the piston head 1 forms together with the channels 5 and the ring channels 6 and 7 the flow path for the pressure side.

The flow path for the rebound side becomes again

through the channels 12, the annular channels 13 and 14 of the piston

8 and the bores 11 and the annular channel 1o of the piston head 1 formed.

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List of reference symbols

1 piston plate

2 second valve seat

3 first valve seat

4 grooves

5 external channels

6 ring channel of the piston (pressure stage)

7 piston ring channel (pressure stage)

8 pistons

9 pressure stage valve

10 ring channel

11 holes in the piston plate

12 bore of the piston

13 piston ring channel (rebound)

14 Ring channel of the piston (rebound stage) 15, 15 'valve disc

16 piston nut

17 valve disc

18 valve nut

19 valve spring

20 - piston foil

21 piston rod

22 Passage of the valve disc 15 '

23 Approach of the piston

24 support pot

25 approach

26 conical outer surface

27 cylinders

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Claims (1)

C · BÖGE GmbH. ·: 'I' .: 'I : 1S *. July 1982 Bogestrasse 5o '"· * * *" 4Vo 52o8 Eitorf St / do s ρ r ü c ti e 1. Hydraulic shock absorber with a working cylinder working piston dividing into two hydraulic chambers, with at least one axially extending hydraulic channel connecting the chambers in the pulling direction, as well as a Hydraulic flow through the channel controlling disc valve, wherein the valve disc with a one radial Provided the flow path limiting throttle passage for permanent connection of the two hydraulic chambers and that the pressurized valve surfaces are open the compression and rebound side are formed by ring channels, the ring channel of the rebound side to the piston towards a smaller distance than the compression side characterized, that on the rebound side axially between the piston (8) and the valve disc (15) a rigid piston plate (1) is arranged, which together with the piston (8) a first (3) and together with the valve disc (15) a forms the second valve seat (2), the diameter of the disk (15) and piston head (1) formed between the valve second valve seat (2) has a larger diameter than that between piston (8) and piston head (1) formed first valve seat (3). ί 41ο h / th I 2. Hydraulic shock absorber according to claim 1, I characterized by ; that the Kolbenteler (1) on its outer periphery ; Channels (4) or a conical outer surface (26) has, with the annular channels (6, 7) and the axial Hydraulic channels (5) on the compression side work together. * work. 3. Hydraulic shock absorber according to claim 1, , characterized, \ that between the outer surface of the piston (8) and on the inner wall of the cylinder (27) a contact seal (2o) clamped to the piston (8), e.g. a plastic ring, PTFE film or the like is arranged.