Patent Application
20120145496
This invention relates to a shock absorber for a wheel suspension of a motor vehicle. The shock absorber according to the invention comprises among other things a control valve, allowing for the shock absorber to be switched back and forth between a soft damping characteristic and a hard damping characteristic. In particular, the invention relates to such a shock absorber that can be switched back and forth between two damping levels of different hardness and which can be used for implementation in small diameter damper tubes.
Furthermore, the invention relates to a valve arrangement for integration into the interior of a damper tube of a shock absorber in order to produce a shock absorber which can be switched back and forth between a soft damping characteristic and a hard damping characteristic.
Shock absorbers for the wheel suspension of motor vehicles, in which the damping force may be varied, have already been available for a long time. For this purpose, various approaches are known from prior art. On the one hand, prior art suggests shock absorbers fitted with continuously variable valves and which allow for the damping force of the shock absorber to be varied continuously. The implementation of such continuously adjustable valves implies some technical effort so that such shock absorbers are comparatively expensive to manufacture.
Besides shock absorbers with continuously adjustable damping force, also known from prior art are shock absorbers wherein a defined arrangement of passive damping valves in conjunction with a control valve allows for setting different damping characteristics. In particular, it is possible to set different damping characteristics for the rebound stage and the compression stage. An example of this kind of motor vehicle shock absorbers with variable damping force is described in document DE 38 03 888 C2.
From document DE 35 18 327 A1, a hydraulic adjustable vibration absorber having the features of the preamble of independent patent claim 1 is known. In the shock absorber known from this document, a damping piston is provided, which is arranged on a pin of a housing screwed onto the piston rod. In DE 35 18 327 A1, this housing is designated by the term “intermediate sleeve”.
The damping piston has damping valves cooperating with flow channels arranged inside the body of the damping piston. Such damping valves are configured so as to have a hard damping characteristic, i.e. so as to produce high damping forces when damping liquid flows through the flow channels. A bypass is provided hydraulically in parallel to the damping piston. Inside the bypass, a bypass valve is arranged. The latter has a soft damping characteristic, i.e. when damping liquid flows through the bypass valve, only a relatively low damping force is generated in comparison with the damping piston.
The bypass valve is arranged on a flow path formed through a transverse bore in the housing, i.e. in the envelope of the “intermediate sleeve”, and a longitudinal bore in the pin supporting the damping piston. Inside the housing, a control valve is provided. The control valve comprises a coil and a valve body made as an armature. When the coil is not energized then the valve body is seated on a valve mating surface, not identified by a reference number in DE 35 18 327 A1, of a component having an H-shaped cross-section, also not designated more in detail. In this state, the control valve is closed (“closed when currentless”). When the coil is energized, the valve body lifts from the surface against the force of the return spring. The damping medium may then flow from the lower working chamber of the shock absorber into the upper working chamber or in the opposite direction through the bypass. Herein, the damping liquid flows through the bypass valve having the soft damping characteristic, so that the shock absorber only generates comparatively low damping forces.
In the closed state of the control valve, however, the bypass is closed so that there is no flow through the bypass valve. The damping liquid then flows through the flow channels in the damping piston and cooperates with the damping valves arranged on the damping piston, which have the hard damping characteristic. Due to this arrangement, the safety-relevant demand of a so-called “fail-safe function” is satisfied. “Fail-safe” means that in case of sudden failure of the electrical power supply of the shock absorber, the damper must generate a hard damping characteristic in order to warrant safe driving stability even at high speeds and e.g. when cornering.
In the design known from DE 35 18 327 A1, the disadvantage is that the valve arrangement disclosed therein is only suitable in a limited way for an implementation in shock absorbers having a small damper tube diameter. By means of the damping valve having the soft damping characteristic, comfortable damping is to be achieved, providing the passengers of the vehicle with a pleasant driving experience. Therefore, the person skilled in the art also designates this valve as a “comfort valve”. Due to the soft plating of the comfort valve, less resistance is opposed to the damping liquid, and thus smaller damping forces are generated. In order to be able to provide a sufficiently large flow section for the soft damping characteristic, even at higher damper speeds, a diameter as large as possible for the comfort valve and the valve disks thereof is targeted. However, in the shock absorbers described in DE 35 18 327 A1, for design reasons, the comfort valve only has a relatively small diameter. Consequently, at least when the damper tube only has a small diameter, it is not possible to design this comfort valve to be large enough to offer sufficient driving comfort and spread between the hard and soft damping characteristics, even at higher damper speeds. Also, the durability of smaller diameter valve disks is significantly lower than for larger diameter valve disks. Moreover, the valve arrangement described in DE 35 18 327 A1 has a large overall axial length due to the cross-section of the H-shaped element on which the armature/valve body of the control valve is sealingly resting.
Another disadvantage of the subject matter of DE 35 18 327 A1 is that, as seen in the axial direction, the damping piston must have a minimum overall height if the shock absorber is to be implemented in a McPherson strut unit. Indeed, in such strut units, the steering movements of the vehicle are introduced via the piston rod of the shock absorber so that the corresponding transverse forces are transmitted via the damping piston to the damper tube. This can no longer be ensured if the damping piston falls short of the minimum overall height. Therefore, in DE 35 18 327 A1, the possibilities for reducing the overall axial height of the damping piston used for the hard damping characteristic are quite limited.
In DE 40 08 326 C1, a hydraulic, controllable vibration absorber is described in which at least three different damping force levels can be set by means of an electromagnetically activated valve. A flow channel is controlled by means of the electromagnetic valve. In order to generate three different damping force characteristic curves, the valve body can be moved between two end positions, wherein the valve body is supported by at least two springs and can be set between the two end positions thereof in at least one intermediate position via a stop and a stop face. In the respective position, the valve body switches a corresponding bypass so that depending on the position of the valve body, a hard damping characteristic, a soft damping characteristic, and an intermediate average damping characteristic is set. Both springs are opposed to the magnetic force so that in the currentless state of the solenoid, both springs move the valve body into the normal position thereof. When the solenoid has been energized for the first time, the valve body is brought to a stop against the first spring, so that in this position, a bypass is switched. In a consecutive larger energization of the solenoid, the second spring is biased so that the valve body can be brought into the end position thereof, with a second bypass being released in this end position.
In the solution described in DE 40 08 326 C1, it is necessary to differentiate energization of the solenoid so that the valve body can be switched to at least three positions including a starting position. Consequently, it is either necessary to control current intensity when energizing the solenoid, or else—as claimed in sub-claim 8 of DE 40 08 326 C1—the solenoid must have at least two different magnetizing coils. Both of the above-mentioned options are in contradiction with a cost-effective shock absorber design.
Furthermore, the constructional configuration of the control valve according to DE 40 08 326 C1 is elaborate and cost-intensive due to the required springs for supporting the valve body and due to the required stop and stop face.
Moreover, in the solution disclosed in DE 40 08 326 C1, the hard damping characteristic is not provided simply by a single damping valve having a hard damping characteristic, but a sporty hard setting of the vibration damper is achieved by an elaborate hydraulic series connection of the valve disk sets called “spring leaves 16, 17”, cf. FIGS. 1 and 2 as well as col. 3, lines 11-14.
Finally, with reference to the solution disclosed in DE 40 08 326 C1, it is disadvantageous that the rise, i.e. the gradient of the damping characteristic curves in the force/speed diagram is fixedly set in the range of low piston rod speeds. Consequently, in the range of low piston rod speeds, this solution does not meet the demand of flexible adaptability of the gradients of the damping characteristic curves to different customer demands.
The invention is based on the object of providing a shock absorber for a wheel suspension of a motor vehicle having a damping force which can be switched back and forth between two damping force levels and which generates a sufficiently soft damping characteristic even with small damper tube diameters at all piston rod speeds, and in which the damping valve arrangement takes up little overall axial length.
In particular, a cost-effective shock absorber for the wheel suspension of a motor vehicle having a small damper tube diameter is to be provided, which can be switched back and forth in spite of the small damper tube diameter thereof between a hard and a soft damping characteristic.
According to the invention, this problem is solved by a shock absorber having the features of patent claim 1. Advantageous developments of the shock absorber according to the invention are specified in the sub-claims.
Furthermore, the invention is based on the object of providing a solution allowing in particular with shock absorbers for a wheel suspension of a motor vehicle having small damper tube diameters to switch the piston rod back and forth between two damping force levels for each moving direction.
This problem is solved by a valve arrangement having the features of patent claim 6. Advantageous developments of the valve arrangement according to the invention are specified in the sub-claims.
The valve arrangement according to the invention is suitable both for use in single tube dampers (single chamber active principle) and in double tube dampers (double chamber active principle).
According to the invention, not only the first damping valve having the soft damping characteristic, but also the second damping valve having the hard damping characteristic, is arranged inside the housing, and the housing forms the element by which the interior of the damper tube is divided into a piston rod-side working chamber and a working chamber remote from the piston rod. Thereby, a conventional damping piston dividing the damper tube into a piston rod-side working chamber and a working chamber remote from the piston rod, which is frequently also called “working piston” and which is implemented in conventional shock absorbers, can be omitted. In the present invention, the damping function of the conventional damping piston providing a hard damping characteristic is moved into the housing, so to speak, by virtue of the arrangement of the second damping valve. Thereby, the designer can minimize the second damping valve with respect to the overall axial height thereof, because it no longer has to transmit transverse forces. In the design according to the invention, transverse forces are transmitted by the housing adjacent to the damper tube. Especially for use in McPherson strut units, which are very frequently implemented in motor vehicles, the inventive solution is thus well suited.
In the design according to the invention, the designer can maximize the housing with respect to the inner and outer diameter thereof, so that, in particular in shock absorbers having a small damper tube diameter, a maximum diameter is available for housing the damping valve having the soft damping characteristic. Thereby, even in shock absorbers having a small damper tube diameter of e.g. 32 mm, a sufficient spread between hard and soft damping characteristics and satisfactory driving comfort can be achieved at all piston rod speeds. Moreover, the durability of the valve disks is significantly improved.
The first and second damping valves are preferably embodied as passive pressure relief valves. It is particularly preferred for said valves to be embodied as spring washer valves.
According to the invention, the first and second damping valves are hydraulically interconnected in parallel.
According to the invention, the valve by which the first damping valve having the soft damping characteristic can be switched from one into the other working chamber on the flow path of the damping liquid, is embodied as a control valve, which can be switched back and forth between a closed and an open position. Advantageously, the control valve can be embodied as an electromagnetic or piezoelectric control valve.
According to a preferred embodiment of the invention, between the first and second damping valves, an element having at least one check valve is arranged. The element may have a check valve through which the damping liquid may only flow when the piston rod moves in one direction. Thus, the flow may pass through the check valve only when the piston rod moves in the direction of rebound, or the flow may pass through only when the piston rod moves in the direction of compression. As a result, it is only when the piston rod effectively moves in this moving direction that an additional bypass channel is available for the damping liquid. This additional bypass channel directs a partial flow of the damping liquid around the damping valves having the soft and the hard damping characteristics. As a result, in this moving direction of the piston rod, a damping force gradient having a smaller rise, i.e. a smaller gradient in the range of low piston rod speeds, than the damping force gradient resulting for the other moving direction appears in the force/speed diagram. Indeed, when the piston rod moves in the other direction, the check valve of the element closes the additional bypass channel so that all of the damping liquid must flow through the damping valves having the soft and hard damping characteristics.
Another effect of the additional bypass channel provided by the check valve of the element is that in the moving direction of the piston rod in which the flow may pass through the check valve, a damping force gradient appears in the force/speed diagram which has a lower rise, i.e. a lower gradient, in the range of low piston rod speeds than the damping force gradient which would result for the same moving direction if the check valve on the element were not there.
Thus, due to the element with the check valve, depending on the moving direction of the piston rod, i.e. separately for the rebound stage and the compression stage, specifically a desired slope of the damping force characteristic curve can be achieved in the range of low piston rod speeds. Indeed, in one piston rod moving direction, an additional bypass channel is available and effective, while it is not effective in the other piston rod moving direction because the flow cannot pass through it due to the check valve being closed.
Also, in the range of high piston rod speeds, the element with the check valve causes a different damping force gradient than what would be available if the element did not have a check valve. This will be explained more in detail below in the description of the practical sample embodiment.
According to another embodiment of the invention, the element arranged between the first and second damping valves has two check valves, wherein the damping liquid may flow through one of them when the piston rod moves in one direction, and through the other one when the piston rod moves in the other direction, wherein the check valves cooperate with bypass channels having different flow sections. In this embodiment, the gradients of the damping force characteristic curves in the compression stage and in the rebound stage are specifically biased independently from each other by the dimensioning of the bypass channels in the element, so that the damping characteristic of the damper can be adapted very flexibly to customer demands.
According to one embodiment of the present invention, the control valve is embodied as an electromagnetic or piezoelectric control valve. It activates a valve body, which in the closed state of the control valve is sealingly seated on a valve mating surface. If the control valve is embodied e.g. as an electromagnetic control valve with a coil and a magnet core, then the valve body preferably is the movable armature of the control valve. Advantageously, the first damping valve having the soft damping characteristic has a peripheral edge forming a valve mating surface for the valve body of the control valve. Thus, no separate component is required to provide a valve mating surface for the valve body on which the latter may rest sealingly. Rather, the valve mating surface is integrated into the damping valve having the soft damping characteristic. Again, this will also reduce or minimize the required axial package space for the valve arrangement. For instance, in comparison with the solution known from DE 35 18 327 A1, in which a component having an H-shaped cross-section forms the valve mating surface, considerable savings in axial package space are achieved thereby.
Hereafter, the invention will be explained more in detail by means of a drawing representing a sample embodiment. In particular,
Inside the housing 5, a first damping valve 7 and a second damping valve 8 are arranged. The first damping valve 7 has a soft damping characteristic, while the second damping valve 8 has hard damping characteristic. The end of the housing 5 facing away from the piston rod 2 is open. Between the second damping valve 8 and the first damping valve 7, an element 9 is arranged. The second damping valve 8 and the element 9 respectively have one center channel 20. The element 9 has a check valve 10. In the represented sample embodiment, the check valve 10 is embodied as a check valve exclusively effective in the compression stage of the shock absorber. This implies that the check valve only opens when the piston rod 2 moves in the direction of compression (i.e. in
Similarly, within the scope of the present invention, it would be possible for the check valve 10 to be embodied as a check valve exclusively effective in the rebound stage. However, in this specific sample embodiment, a check valve through which a flow may pass exclusively in the compression stage is assumed as this is the case of application most frequently encountered. As already mentioned above, it is also possible to arrange two check valves 10 on element 9, with the flow passing through one of them in the direction of rebound and through the other in the direction of compression. Each check valve cooperates with a bypass channel 35 associated therewith. Appropriately, both bypass channels have different dimensions in order to achieve a different influence of the damping characteristic curves in the rebound stage and the compression stage.
Furthermore, the valve arrangement disposed inside the housing 5 comprises a control valve 6. In the represented sample embodiment, the control valve 6 is embodied as an electromagnetic control valve. It comprises an electromagnetic coil 21, a magnet core 22, and an armature 23. In the represented sample embodiment, the armature 23 is formed by the valve body 11. A helical compression spring 24 is arranged between magnet core 22 and valve body 11. The helical compression spring 24 acts as a return spring, against the compression force of which the valve body 11 can be lifted by the magnetic force of the solenoid. When the electromagnetic control valve 6 is not energized, then the helical compression spring 24 pushes the valve body 11 into the closed state thereof, so that the valve body 11 is sealingly seated on the valve mating surface 13. Thereby, the so-called fail-safe function is ensured, i.e. in case of a sudden power outage, the control valve will be in the closed state, so that the first damping valve 7 having the soft damping characteristic does not receive any damping liquid flow, and only the second damping valve 8 having the hard damping characteristic causes the damping characteristic.
The operating mode of the valve arrangement according to the invention will be described more in detail hereafter by means of three selected operating states.
In the operating state represented in
As indicated by the dashed and continuous lines and arrows, when the control valve 6 is closed, damping liquid may only flow through the second camping valve 8 having the hard damping characteristic. In
When the housing represented in
When the housing 5 moves in the direction of compression (i.e. in
Openings 40 are arranged while being distributed over the periphery of the housing 5, through which openings the damping liquid may flow into the housing 5 (rebound stage) or out of the housing (rebound/compression stage).
In
In line with
If the housing 5 moves in the direction of rebound and the control valve 6 is open, as represented in
The second damping valve 8 having the hard damping characteristic stays closed, because at low piston rod speeds, the opening pressure of the pressure relief valve 30 is not exceeded.
However, when the housing 5 moves in the direction of compression, the damping liquid volume flow splits into a total of four partial volume flows. The largest partial volume flow flows through the pressure relief valve 51, which is arranged on the first damping valve 7. A smaller partial volume flow flows through the permanently open bypass channel 52 of the first damping valve 7. Another partial volume flow flows through the permanently open bypass channel 31, which is arranged in the second damping valve 8. A fourth partial volume flow flows through the check valve 10 arranged on element 9, which exclusively opens when the housing 5 moves in the direction of compression. Thus, when the housing 5 moves in the direction of compression, due to the additional bypass channel in element 9, a larger flow area is available for the damping liquid than when the housing 5 moves in the direction of rebound. Consequently, for the compression stage of the shock absorber according to the invention a different gradient of the damping characteristic curve can be achieved than for the rebound stage. Specifically, in the compression stage, a lower damping force is obtained than at the same housing speed in the rebound stage.
In the operating state represented in
In
Again, the dashed lines mark the flow conditions when the housing 5 moves in the direction of rebound, i.e. in
It is clearly apparent that the damping valves 7 and 8 are arranged hydraulically in parallel to each other.
In the third operating state according to
When the housing 5 moves in the direction of compression, i.e. in
Thus, it should be noted that even in operating state 3 for a moving direction of the housing 5 in the direction of compression, due to the check valve 10 arranged in element 9, a larger flow area is available for the damping liquid than when the housing 5 moves in the direction of rebound. Consequently, again in the compression stage, a different damping force gradient is achieved than in the rebound stage.
In
The damping characteristic curve designated by the letter C is a damping force characteristic curve which would occur if element 9 had no check valve and thus no additional bypass cross-section 35 effective in the compression stage were available. It is clearly apparent that in this case, in the range of low piston rod speeds, the slope of the damping force characteristic curve C is the same as for the rebound stage characteristic curve A.
A comparison of both gradients of characteristic curves B and C shows that by providing the additional bypass cross-section 35 by means of the check valve 10 on element 9, lower damping forces are achieved at defined piston rod speeds than if element 9 had no check valve.
The representation according to
In the damping valve arrangement according to the invention, several different provisions minimize the axial package space necessary for the valve arrangement.
On the one hand, the axial package space of the valve arrangement according to the invention is minimized in that the damping valve 8 having the hard damping characteristic has been integrated into the interior of the housing 5, while the housing 5 has been designed in terms of diameter thereof so that the piston band 14 arranged on the housing 5 performs dividing of the damper tube interior into a piston rod-side working chamber 3 and a working chamber 4 remote from the piston rod. Thereby, in particular with McPherson strut units, the required force transmission, from the piston rod 2 to the damper tube 1 can take place via the housing 5. In conventional shock absorbers, this function is usually performed by the working piston which for this purpose must not fall short of a defined minimum overall height. In conventional shock absorbers, the working piston then usually also has the hard damping characteristic. Thus, in conventional shock absorbers, the overall axial height of the damping element which is in charge of the hard damping characteristic (namely the working piston) must not be reduced below a defined dimension. In the valve arrangement according to the invention, however, the second damping valve 8 in charge of the hard damping characteristic can be minimized with respect to the overall axial height thereof, because it is not necessary for the same to be available for force transmission from the piston rod to the damper tube. As explained, this force transmission is performed exclusively via the housing 5.
On the other hand, axial package space in the valve arrangement according to the invention was saved in that the valve mating surface 13, on which the valve body 11 is sealingly seated in the closed state, is not formed by a separate component, but is integrated into the first damping valve 7. For this purpose, the first damping valve 7 has a peripheral edge 12 forming the front surface of the valve mating surface 13 for the valve body 11. Thus, no separate component connected to the housing 5 or radial protrusion of the housing 5 is required to provide a valve mating surface for the valve body 11. This again saves axial package space. In particular, in comparison with the solution mentioned at the beginning according to DE 35 18 327 A1, significant axial package space saving is obtained because the component having an H-shaped cross-section, known from DE 35 18 327 A1, requires considerable axial package space. The inventive valve arrangement, however, is very compact in the axial direction.
In the valve arrangement according to the invention, element 9 is integral with the housing 5. Thereby, the first damping valve 7 is solidly clamped between element 9 and radial protrusion 72 of the housing 5.
Due to the damping element according to the invention, a conventional shock absorber having a conventional damping piston fastened to the piston rod can be easily converted into a shock absorber which can be switched back and forth between two different damping characteristics (hard damping/soft damping). All that is required for this purpose is for the conventional damping piston to be removed from the piston rod and the housing 5 of the valve arrangement according to the invention to be fastened to the piston rod. The required power supply for operating the electromagnetic control valve 6 is done using a hollow piston rod, through the cavity of which the required cables are guided.
The valve arrangement according to the invention allows for the housing 5 to be made with a maximized inner diameter with respect to the damper tube inner diameter, so that the damping valves 7 and 8 can have a maximum diameter. This is important in particular for designing the first damping valve 7 having the soft damping characteristic. In order to achieve a damping effect which will increase driving comfort at all piston rod speeds and maximize the spread between the hard and soft damping characteristics, in particular with shock absorbers having small damper tube diameters, a maximum diameter for the damping valve with the soft damping characteristic must be provided. In the valve arrangement according to the invention, this is achieved in an exemplary manner.
| Number | Date | Country | Kind |
|---|---|---|---|
| 10 2009 038 818.4 | Aug 2009 | DE | national |
| Filing Document | Filing Date | Country | Kind | 371c Date |
|---|---|---|---|---|
| PCT/EP10/05152 | 8/23/2010 | WO | 00 | 1/11/2012 |
