JPS6151179B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention is a vibration damper having elements whose damping action varies in relation to speed, comprising a fluid-filled cylinder in which a restricted A piston is guided which is connected with axial movement to the piston rod, which piston is loaded by a spring and which divides the cylinder interior into two working chambers, and which The two working chambers can communicate with each other via a passage acting as a damping valve, and the piston is configured as an axially movable valve element and together with a throttle element provided on the piston rod, the piston of the type forming a damping cross-section which is varied in the direction of movement.

The known vibration damper is provided for a vibration damper of a washer drum which is elastically suspended on the washer casing and acts in accordance with the frequency of the vibrations associated with the piston rod. A substance is placed and deflected from a predetermined rest position against a return force. The substances associated with such vibrations communicate with the two working chambers separated by the piston and cooperate with the outlet of the hole system extending through the piston rod, and are transmitted to varying degrees depending on the frequency. but strongly closes this outlet, whereby the damping force is controlled in relation to the frequency.

The object of the invention is to construct a vibration damper in a simple manner and in such a way that the damping force increases with increasing speed and/or acceleration of the piston rod.

In order to solve such problems, the present invention
A spring presses the piston against the stopper disc,
In addition, at this piston position, an open buffer cross section is formed between the piston and the throttle member provided on the piston rod, and furthermore, when the piston rod is moved in one direction, the external force absorbs the force of the spring. If exceeded, the damping cross section is reduced, and an overpressure valve is provided which opens when the piston rod is moved in the same direction as the movement direction.

The fluid is under pressure within the cylinder interior. This means that the vibration damper also has a spring function.

The fluid is a liquid, with which the elastic compensation element in the cylinder interior is in contact. The elastic compensation element is brought into contact with the liquid by means of a movable partition. The elastic compensation element contains a spring as an elastic medium and acts on the spring partition.

The return force acting on the piston is created by a piston action spring, which holds the piston in a rest position on the piston rod.

The vibration damper according to the invention is particularly defined and suitable for increasing the damping force by increasing the speed and/or acceleration of the piston rod. Of particular importance in the embodiment is that the damping force is largely speed-related. In consideration of such problems, the vibration damper of the present invention is further proposed as follows. That is, the movement of the piston is such that, upon movement of the piston rod in a first direction, the cross section of the throttle point is reduced in relation to the magnitude of the velocity and/or acceleration of the piston rod in this direction. The resistance and the return force of the spring are matched to each other, and the aperture surface is arranged in such a way.

The vibration damper according to the invention is constructed such that when the piston rod moves into the cylinder, the damping force increases in the direction of the piston movement due to an increase in velocity or acceleration. However, it can also be provided that the damping force increases as the piston rod moves out of the cylinder due to an increase in speed and/or acceleration. Of course, embodiments are also possible in which the increase in the damping force when the piston rod moves into or out of the cylinder is associated with an increase in velocity and/or acceleration in each direction. It is possible. In an advantageous embodiment, it is provided that the cross section of the throttle point is independent of velocity and acceleration during movement of the piston rod in a second direction opposite to the first direction.

Piston movement resistance is caused by various reasons. If the movement resistance is based largely on the mass of the piston, the damping force is largely related to the acceleration. If the movement resistance is largely due to the friction of the piston on the cylinder wall, and this friction is speed-related, then the damping force of the vibration damper is also speed-related. If the motion resistance in the piston is based on the flow resistance due to flowing liquid through the piston, and this flow resistance is velocity related, then the magnitude of the damping force is also velocity related.

The resistance to motion in the piston is related to the amount of fluid flow through the piston, as the piston has a fluid flow region that is constricted and the fluid flow region has an axial movement within the cylinder associated with the movement of the piston. It is obtained by limiting the motion resistance against. Such a throttled flow section is preferably connected independently of the throttle cross-section of the throttle point and alongside the throttle point.

A continuous increase in the damping force of the vibration damper according to the invention is achieved in that the piston-side throttle surface and the piston rod-side throttle surface are designed as conical surfaces.

An overpressure valve is provided between both working chambers, which limits the increase in damping force as the speed and/or acceleration of the piston rod increases. Due to the provision of such an overpressure valve, the vibration damper according to the invention is particularly suitable for integration into ski bindings. In this case, the vibration damper is engaged in a binding element, which in normal operation is held in a rest position by spring force approximately on the pivoting clamp of the safety binding. The spring force in this case is provided by a vibration damper. During slow swivel movements, the binding member is hardly supported by the damping force provided by the vibration damper. In the case of very sudden vibrations, on the other hand, the binding element is additionally supported by an increased damping force. Overpressure valves are effective when very large forces are applied that cause the binding members to disengage. Manual adjustment of the binding member, which is carried out relatively slowly, is practically unimpeded by the vibration damper. Since the preconditioning is provided by the magnitude of the damping force produced by the vibration damper according to the invention, the maximum damping force is 800N. If the buffering force exceeds 800N, an overpressure valve acts as a safety valve. The overpressure valve is formed by the part of the throttle point. This advantageously provides that the piston rod-side throttle surface is formed in a throttle element, which throttle element is movable along the piston rod against a spring force and is designed as a valve element of the overpressure valve. This is achieved by

Moreover, the overpressure valve is arranged parallel to the connecting channel.

The invention will be explained below with reference to the exemplary embodiments shown.

The vibration damper shown in FIG. 1 consists of a cylinder 1 in which a piston 5 arranged on a piston rod 2 is arranged axially movably against the return force of a piston-actuating spring 10. . cylinder 1
A partition wall 3 guiding the piston rod 2 at the outlet end of the piston rod 2 is loaded by a spring 14, so that this partition wall 3 cooperates with the piston rod sealing element 4 and adjoins the working chamber 6. An elastic compensation element is formed, which compensates the entry or exit volume of the piston rod into the working chamber 6. A working chamber 6 and a working chamber 7 are connected to each other via a hole 8 provided in the piston 5 and forming a throttle passage. A throttle element 11 is guided movably in the axial direction along the piston rod 2, the spring force of a spring 13 being supported on one side by a stop connected to the piston rod and on the other side by the throttle element 11. be done. A spring 10, which loads the piston 5, is supported on one side in a stop formed, for example, by a retaining ring and arranged in the groove of the piston rod; A stopper is also formed for this purpose. Furthermore, a stop disk 15 for the piston 5 is provided at the end of the piston rod.

In the illustrated position of the vibration damper, an annular gap as a damping cross section is present between the piston-side throttle surface 9 of the piston 5 and the piston-rod-side throttle surface 12 of the throttle element 11. This annular gap forms a constriction point located in the connecting channel 26 between the two working chambers 6 and 7. When the piston rod 2 moves rapidly or slowly, such an annular gap is not changed, so that this movement takes place practically undamped, in which case the liquid flows into the working chamber 6.
from there to the working chamber 7 via an annular gap and a hole 8 . Both working chambers 6, 7 are completely filled with liquid working medium. The volume changed from the working chamber 6 during the moving in and out movement of the piston rod 2 is
It is compensated by the partition wall 3 which is under the action of a spring 14 and is movable within the cylinder.

When the piston rod 2 moves into the cylinder 1, the damping force is dependent on the speed of entry. This is because when the piston rod 2 moves slowly in the cylinder 1, the annular gap formed between the throttle face 9 and the throttle face 12 remains open and the buffer liquid flows from the working chamber 7 to the bore 8 and the annular gap. This is because it flows into the working chamber 6 via 9 and 12. At relatively high entry speeds, such an annular gap between the throttle surface 9 and the throttle surface 12 is reduced. This is because the piston 5 is subjected to movement resistance and the piston action spring 10 is therefore compressed. The movement resistance of the piston is related to various factors: the mass of the piston 5, the friction of the piston 5 on the inner surface of the cylinder and the flow resistance in the bore 8. When the piston rod 2 moves in very rapidly, the annular gap between the throttle face 9 and the throttle face 12 is completely closed, so that a high damping effect occurs. If the force acting on the damper exceeds a predetermined maximum damping force of, for example, 800 N, the throttle element 11 is likewise moved axially on the piston rod 2 against the force of the spring 13, thereby causing Piston 5 and throttle member 11
A gap is again formed between the working chamber 7 and the working chamber 6, so that liquid flows from the working chamber 7 into the working chamber 6 via the hole and the annular gap 9. This ensures that the binding can be released under heavy loads, for example in the case of ski binding. A throttle element 11 with a spring 13 forms part of the overpressure valve, the opening of the overpressure valve being defined by the force of the spring 13.

The embodiment according to FIG. 2 differs from the embodiment according to FIG. . Ball 116 is compression spring 1
25. overpressure valve 116,
125 is a vertical hole 117 and a horizontal hole 118 so that both working chambers 106 and 107 communicate with each other and the connecting passage 12
6, and the connecting passage 126 has throttle gap 109,112. A throttle element 111 is in this case fixedly arranged on the piston rod 102. The vibration damper according to FIG. 2 differs from the vibration damper according to FIG. 1 in function only when the piston rod 102 is inserted into the cylinder 101; Unfortunately, the gap 109,1 that exists between the throttle member 111 and the piston 105
12 is closed by the axial movement of the piston 105 towards the throttle member 111 against the force of the piston action spring 110. When only the force acting on the vibration damper rises above the predetermined maximum damping force, the overpressure valves 116, 125 open and the damping liquid flows from the working chamber 107 into the working chamber 106 through the vertical hole 117 and the horizontal hole 118. flows to When the force acting on the damper falls below the maximum damping force, the piston 105 is lifted from the throttle member 111 by the force of the spring 110 and the annular gap 109, 112 between the piston and the throttle member 111 is re-created. Therefore, when the insertion movement of the piston rod 102 is slow, the buffer liquid flows from the working chamber 107 into the working chamber 106 via the hole 108 formed in the piston 105 and the annular gaps 109, 112.

In the embodiment of FIG. 3, the running movement of the piston rod 202 from the cylinder 201 produces a damping effect that is dependent on the speed. In this case, the piston 205 moves in the axial direction relative to the piston rod 202 during the running movement of the piston rod 202, and the piston 205 moves in the axial direction relative to the piston rod 202 during the running movement of the piston rod 202.
The annular gap formed between 09 and the aperture surface 212 is closed. In this case too, the piston 205 acts against the force of the spring 210. When the predetermined maximum damping force is below, the annular gap 209, 212 opens and the buffer liquid flows from the working chamber 206 into the working chamber 207 via the hole 208 and the annular gap 209, 212. The piston rod guide part 203 and the piston rod seal member 204 are arranged immovably in the axial direction at the piston rod outlet side end of the cylinder 201,
On the one hand, the compensating element consists of a partition wall 219 which is arranged in the area of the cylinder bottom for the incoming or outgoing piston rod part and is loaded by a spring 220.

When the force acting on the piston rod 202 exceeds the predetermined maximum buffering force, the safety valves 216, 225 open and the buffering liquid flows from the working chamber 206 to the lateral hole 218.
and flows into the working chamber 207 via the vertical hole 217.

The invention is not limited to the illustrated embodiment, but can be varied in construction, for example, the throttle element 211 is formed as a cylindrical configuration, in which case the throttle element forms a conical throttle of the piston 205. cooperates with the surface 209 and as a result the diaphragm member 21
1 and the piston 205 is nozzle-shaped. Furthermore, the damping cross section can likewise be formed by the end face of the piston 205 cooperating with the end face of the throttle element 211 . It is also possible with a simple design to adjust the overpressure valves 216, 225 to the desired values. This is because the initial spring force of the compression spring loading the valve ball member 216 is present at the end of the piston rod 202 at the tightening nut 22.
This is because it is changed by 7.

A ski 30 is shown in FIG. This ski is provided with a front binding 31 of the safety binding. Front fastener 31
can be turned around the turning bolt 32.
A pair of skis 33, shown in broken lines, is crimped onto the front binding 31 by means of a heel piece (not shown). In the event of a dangerous fall, the ski shoe will shift in the direction of the double arrow 34. This is because the front fastener 31 is rotated around the rotation bolt 32. The front clamp is held stationary by a vibration damper according to the invention, the cylinder 1 and piston rod 2 of which are shown.
The cylinder 1 is rigidly fixed to the ski 30. The piston rod 2 engages with a spherically rounded tip 35 in a ball section 36 formed at the top of the front clamp 31 . The vibration damper according to the invention acts as a spring which prevents the front clamp 31 from flexing during normal operation, but causes the front clamp 31 to flex in case of overload. While the front clamp 31 is rotated and the piston rod 2 is pushed into the cylinder 1 against the spring force, the ball tip 35 slips off the ball section 36. When the front clamp 31 is rotated slowly, the piston rod 2 is moved against the partition walls 3, 4 and the spring 1.
4 into the cylinder 1 against the spring force exerted by 4. The front clamp 31 can therefore be adjusted loosely by hand. High-frequency rotational vibrations cause the front fastener 3
1, the front clamp 31 causes the piston rod 2 to undergo correspondingly high-frequency, ie rapid, axial vibrations. However, since the throttle gap 9, 12 is closed, the vibration damper according to the invention resists a rapid axial entry movement of the piston rod 2. Therefore, in the case of such high-frequency vibrations, the piston rod 2 is not only pushed into the cylinder against the elastic resistance when the front clamp 31 is rotated, but also the piston rod 2 is pushed into the cylinder against the elastic resistance. Despite resisting the damping force, the throttle gap 9, 12 is moved closer and tighter by the increasing speed of the piston rod 2. If the front clamp 31 is rotated to release the binding, the overpressure valve opens only when the force on the piston rod 2 reaches a predetermined maximum value.

Assume that the vibration damper has a maximum stroke of 10mm. The buffering force increases to 800N. The vibration damper is constructed in such a way that the damping force increases up to 800N with increasing speed of the piston rod, and above 800N the overpressure valve opens. In short, for example
The damping force is greatest at very small piston rod oscillation distances of 0.2 mm and high piston speeds. Nevertheless, the safety binding is prevented from disassociating by means of an overpressure valve. In this case, no damping force is actually generated, so that the front clamp 31 can be rotated by hand.

The vibration damper according to the invention can be made to act only as a vibration damper without at the same time fulfilling an essential spring function. For example, the vibration damper can be arranged parallel to the spring in the embodiment according to FIG. The use for ski binding is not limited to the embodiment according to FIG. 4. The vibration damper according to the invention ensures that the ski binding parts are not moved by high-frequency vibrations below a predetermined force, but become disengaged above this predetermined force.

[Brief explanation of the drawing]

FIG. 1 is a vertical sectional view showing a first embodiment of a vibration damper according to the present invention, FIG. 2 is a longitudinal sectional view showing a second embodiment, FIG. 3 is a longitudinal sectional view showing a third embodiment, and FIG. 4
The figure is a plan view of a case where the vibration damper of the present invention is combined with a ski binding. DESCRIPTION OF SYMBOLS 1... Cylinder, 2... Piston rod, 3... Partition wall, 4... Piston rod sealing member, 5... Piston, 6, 7... Working chamber, 8... Hole, 9... Throttle surface, 10 ...Spring, 11...Aperture member, 12...
Aperture surface, 13, 14... Spring, 15... Stopper disc, 26... Connection passage, 30... Ski, 31
……Front fastener, 32 ……Loading bolt, 33
...ski shoes, 34...arrow, 35...tip,
36...Spherical section, 101...Cylinder, 102...
... Piston rod, 105 ... Piston, 106,1
07... Working chamber, 108... Hole, 109... Throttle gap, 110... Spring, 111... Throttle member, 112... Throttle gap, 116... Overpressure valve, 117... Vertical hole, 118... Horizontal Hole, 201...
...Cylinder, 202...Piston rod, 203...
Piston rod guide section, 204... Piston rod seal member, 205... Piston, 206, 207...
Working chamber, 208...hole, 209...diaphragm surface, 21
0...Spring, 211...Aperture member, 212...Aperture surface, 216...Safety valve, 217...Vertical hole, 21
8...Horizontal hole, 219...Partition wall, 220...Spring, 225...Overpressure valve, 227...Tightening nut.

Claims (1)

[Scope of Claims] 1. A vibration damper with a member whose damping action varies in relation to speed, consisting of a fluid-filled cylinder in which there is limited axial movement. A piston is guided, which is connected to the piston rod with are able to communicate with each other via a passage acting as a damping valve, and the piston is configured as an axially movable valve element and together with a throttle element provided on the piston rod in the direction of movement of the piston. In a version that forms a variable damping cross-section, the spring 10 is connected to the piston 5.
is crimped onto the stopper disc 15, and at this piston position forms an open buffer cross section between the piston 5 and the throttle member 11 provided on the piston rod, and furthermore, the piston rod 2 When the external force exceeds the spring force of the spring 10 when the piston rod is moved in one direction, the damping cross section is reduced, and when the piston rod is moved in the same direction as the movement direction, the damping cross section is reduced. A vibration damper characterized in that an overpressure valve 11, 13; 116; 216 is provided. 2. The vibration damper according to claim 1, wherein the fluid inside the cylinder is under pressure. 3. The vibration damper according to claim 2, wherein the fluid is a liquid. 4. The vibration damper according to claim 3, wherein the liquid-elastic compensating members 3, 14 are adjacent to each other in the cylinder interior. 5 Partition wall 3 with movable elastic compensation members 3, 14
Claim 4 adjoining the liquid by
Vibration damper as described in section. 6. The vibration damper according to claim 5, wherein the elastic compensation members 3, 14 have a spring 14 as an elastic member, which spring acts on the partition wall 3. 7. The vibration damper according to claim 1, wherein the piston 5 is held on the piston rod 2 in a static position by a piston action spring 10. 8 Movement of the piston 5 in such a way that, upon movement of the piston rod in the first direction, a cross-sectional reduction of the throttling points 9, 12 occurs which is related to the magnitude of the velocity or acceleration of the piston rod 2 in this direction. 2. Vibration damper according to claim 1, in which the resistance and the return force of the spring 10 are matched to each other and the throttle surfaces 9, 12 are arranged. 9. Vibration damper according to claim 8, in which a reduction in the throttle cross section occurs when the piston rod 2 enters the cylinder 1. 10. Vibration damper according to claim 8, in which a reduction in the throttle cross section occurs when the piston rod 202 moves out of the cylinder 201. 11. According to claim 8, when the piston rod 2 moves in a second direction opposite to the first direction, the cross section of the throttle points 9, 12 is not velocity- and acceleration-dependent. Vibration buffer. 12. The piston 5 has a throttled fluid passage 8, which fluid passage defines a kinematic resistance associated with the movement of the piston against axial movement within the cylinder 1. Vibration damper as described in section. 13. The vibration damper according to claim 12, wherein the constricted flow section is connected to the constriction points 9, 12 independently of the constriction cross section and alongside the constriction points. 14. The vibration damper according to claim 1, wherein the piston-side throttle surface 9 or the piston rod-side throttle surface 12 is formed as a conical surface. 15 Overpressure valves 11, 13 are connected to both working chambers 6, 7
2. A vibration damper according to claim 1, wherein the overpressure valve limits the increase in damping force as the speed or acceleration of the piston rod increases. 16 Overpressure valves 11 and 13 are connected to throttling points 9 and 12
16. The vibration damper according to claim 15, wherein the vibration damper is formed by a portion of. 17 Patent in which a piston rod-side throttle surface 12 is formed on a throttle member 11, which throttle member is movable along the piston rod 2 against a spring force 13 and is designed as a valve member of an overpressure valve. The vibration damper according to claim 16. 18 Overpressure valves 116 and 125 are connected to connection passage 126
16. The vibration damper according to claim 15, wherein the vibration damper is arranged parallel to the . 19. The vibration damper according to claim 1, which is formed as a member of a ski binding.