Abstract:
Shock absorber comprising a piston inside which a sleeve is present which can be operated separately from the piston. This sleeve is provided with through-flow conduits which can cooperate with apertures, which are fitted at a vertical distance, of a part of the piston in order to provide an auxiliary flow when the piston is displaced in the cylinder. Such auxiliary flow enters into a chamber which is delimited by one or more spring plates which act on a sleeve which loads the main valve against opening when it is pressed down by the spring plate. By filling the chamber with fluid, the load applied on the sleeve by the spring plate is reduced and the load on the main valve decreases, as a result of which the latter opens more readily.

Description:
TECHNICAL FIELD 
     The present invention relates to a shock absorber according to the preamble of claim  1 . 
     BACKGROUND 
     More particularly, the present invention relates to an adjustable shock absorber, that is to say a shock absorber whose damping characteristic can be influenced while driving. From the prior art, designs are known in which the pressure on the main valve is influenced by sending an auxiliary flow to the piston. The known designs have the drawback that they need a particularly high adjustment speed which requires complicated electronics. In addition, sensors have to be fitted both to the wheel and to the body of the vehicle. Systems of this type which require large numbers of sensors are highly vulnerable and demand a great deal of expertise during fitting and/or maintenance. 
     SUMMARY 
     DE 1455823 discloses a shock absorber whose damping characteristic can be changed during use. By displacing fluid in an auxiliary conduit, damping becomes increasingly stiff with progressive movement. By pumping increasingly more fluid into a dedicated space as strokes are being carried out repeatedly, the shock absorber becomes increasingly stiff. The reaction of the characteristic of the shock absorber is relatively slow and is influenced for a number of strokes in the direction in which stiffness increases. The reduction takes place gradually over a number of strokes. 
     It is an object of the present invention to provide a relatively simple shock absorber by means of which the damping characteristics can be influenced particularly rapidly. 
     This object is achieved with a shock absorber having the features of claim  1 . 
     CLAIM OF PRIORITY 
     This application is a 371 of International Patent Application No. PCT/NL2010/050625, entitled “ADJUSTABLE SHOCK ABSORBER” by de Kock, filed Sep. 27, 2010, which claims priority to NL2003571 filed Sep. 29, 2009, which applications are herein incorporated by reference. 
     According to the present invention, the pressure on the main valve is applied by a pressure element, such as a sleeve, and said pressure element is pressurized by means of an auxiliary valve which is embodied as a plate spring. In the closed position, said auxiliary valve can provide complete sealing, resulting in an on/off situation. However, it is also possible for a constantly open aperture to be present parallel to said auxiliary valve, a so-called constant, which makes continuously adjustable control possible. The above-described non-return valve is necessary when a parallel aperture is present. This is the case particularly when such a parallel aperture, which connects both sides of the piston, is an aperture which can significantly influence the damping. This is due to the fact that for a rapid reaction, according to an advantageous embodiment of the invention, an aperture of considerable dimensions is desired, so that the built-up pressure can be reduced again quickly. The pressure element and auxiliary valve delimit a part of a chamber into which auxiliary fluid can flow. As more fluid flows into said chamber, the pressure which is exerted on the pressure element by the auxiliary valve will be reduced and thus the pressure on the main valve will decrease. The fluid which flows through the auxiliary conduit and the auxiliary valve is quickly carried away via an aperture so that the above-described accumulation of pressure via a number of strokes known from the prior art does not occur. This results in a particularly rapid adjustment which may lead to a modified characteristic with each stroke and even with each partial stroke of a shock absorber. More particularly, according to a particular embodiment of the invention, the flow in the chamber can be influenced by means of a bush which is present in the piston and can be displaced with respect thereto. This bush provides a bypass conduit. This bypass conduit for auxiliary fluid also extends through two spaced-apart apertures in the piston. By moving the position of the bypass conduit in the bush with respect to the apertures in the piston, it is possible to achieve a greater or smaller choking effect, as a result of which the effect of the reduction of the pressure on the main valve can be influenced. Operation of the bush can be effected in any conceivable way. Thus, it is possible to embody the piston rod to be hollow and thus to provide an actuating rod for the bush. This can be operated by hand, electrically or in any other conceivable way at the top end of the piston rod. However, it is also possible to install wiring in the hollow piston rod which actuates a coil which is fitted near the piston and which then determines the position of the bush. With electrical embodiments, it is possible to rapidly adjust the characteristic for each stroke of the shock absorber or even during the movement of the shock absorber. Such an electrical embodiment can be realized relatively simply and requires few vulnerable parts. 
     The above-described principle of controlling the preload on the main valve by using an auxiliary valve for loading, the applied force of which is reduced when the fluid flow is present, can be used both in a direction of movement of the piston with respect to the cylinder and in both directions of movement of the piston with respect to the cylinder. In addition, the bush in combination with the delimiting part of the piston in which the apertures are provided can be configured such that when the auxiliary flow is influenced in two directions when the passage for the auxiliary flow in one direction is enlarged, the auxiliary flow in the other direction is, on the contrary, throttled more. If sufficient flow through the auxiliary conduit can be effected affected, it is possible by means of the above-described electrical control mechanism to influence the damping characteristic during the stroke. This variant, if configured as an electrical device, also consists of a particularly simple construction comprising few vulnerable components and exhibiting great operational reliability. By means of the present invention, it is possible to achieve a so-called “sky hook”-characteristic, without using specific sensors such as employed in the prior art to be able to influence the shock-absorbing performance during a damping stroke. 
     Just like the main flow, the auxiliary flow extends along both sides of the piston and therefore, a non-return valve can be present therein. Such a non-return valve may be a separate valve, but may for example also form part of the main valve. 
    
    
     
       BRIEF DESCRIPTION OF THE DRAWINGS 
       The invention will be explained in more detail below with reference to a number of exemplary embodiments, in which: 
         FIG. 1  diagrammatically shows a shock absorber according to the present invention, 
         FIG. 2  shows a first exemplary embodiment of the piston illustrated in  FIG. 1 . 
         FIGS. 3A-3C  show a further example of the piston illustrated in  FIG. 1 . 
         FIG. 4  shows a further variant of the bush used in the piston. 
         FIG. 5  shows a further embodiment of the non-return valve used for the auxiliary flow. 
     
    
    
     DETAILED DESCRIPTION 
       FIG. 1  diagrammatically shows a shock absorber which is denoted overall by reference numeral  1 . It consists of a cylinder  2  and a reciprocating piston  3  which, via a piston rod  4 , is connected to a fastening means which is not shown in detail. Piston  3  and cylinder  2  are attached to the various parts which are to be damped with respect to one another of, for example, a vehicle. 
     Details of a first embodiment of the piston  3  can be seen in  FIG. 2 . The piston  3  comprises a core  5  which is fixedly connected to the piston rod  4 . This core comprises a cavity  21  in which a bush  6  can be rapidly moved to and fro. This bush  6  is hollow and provided with spaced-apart apertures  7  and  8 . Bush  6  can be moved to and fro in the direction of arrow  10  with respect to the piston rod  4  by means of the rod  9  which is connected thereto and which can move to and fro inside the piston rod  4 . Displacement can be effected, for example, by means of a piezo element, coil, rotating stepping motor, manually and the like. In the illustrated position, the apertures  7  and  8  are in front of the apertures  11  and  12 , respectively. By displacing the bush with respect to the piston, the through-flow passage between apertures  7  and  11 , and  8  and  12 , respectively, can be enlarged or reduced. A spring  13  loaded valve  22  is present in the flow path for fluid indicated by line  23 . 
     Around core  5 , ring parts  14  and  25  are provided which are fixedly connected to core  5 . Between the ring parts  14  and  25 , a main valve  18  is provided which comprises a spring-mounted plate. It seals a bore  26  against the passage of the flow denoted by reference numeral  27 . The resistance of the valve  18  to being opened is partly determined by the pressing of the bottom  20  of a sleeve  15  which is fitted around the ring part  25  so as to be displaceable with respect thereto. As can be seen in  FIG. 2 , this sleeve  15  is pushed down by a spring plate  16 . That is to say that the force which the spring plate  16  exerts on the sleeve  15  and thus on the bottom  20  thereof determines the opening characteristics of the main valve  18 . As the spring plate  16  seals completely in this exemplary embodiment, an on/off situation arises when reducing the prestressing force on the sleeve  15 . 
     Between the ring part  25  and the bottom  20  of the sleeve  15 , there is a chamber  17  which is at the same pressure as the part of the cylinder  2  situated above the piston  3 . 
     When the piston moves down in the cylinder, the above-described embodiment functions as follows: 
     The main stream indicated by reference numeral  27  experiences a resistance from the main valve  18  which is determined by the pressure of the ring  20  of the sleeve  15  and thus by the force of spring plate  16 . If a prolonged downward movement takes place and the bush  6  is positioned such that flow path  23  is open, pressure will build up in chamber  28 . This build-up of pressure is counteracted by the aperture  24 . The balance between influent fluid/discharged fluids determines the build-up of pressure in the chamber. When pressure builds up, the downward closing force of spring plate  16  on the sleeve  15  will decrease. As a result thereof, the bottom  20  of sleeve  15  will press on the main valve  18  with less force, thus opening a larger aperture to the main flow  27 . By moving the bush  6  upwards, a throttling effect can be achieved between the apertures  7 - 12  and  8 - 11  and, if desired, complete sealing can be effected. In this manner, the damping characteristic can be adjusted in a particularly simple way. It is possible to change the damping characteristic in a simple manner by adjusting the sleeve  15  and more particularly the bottom  20 . 
     This is due to the fact that, if the point of contact of the main valve  18  with respect to bottom  20  is moved, the stiffness of the opening part of the main valve  18  will change due to the fact that the free end of the main valve  18  becomes longer or shorter. Thus, the optimum setting for the respective vehicle can be found in a simple and reproducible way. 
     The above-described effect of influencing the main valve  18  by means of a secondary fluid flow  23  which reduces the prestressing force of said valve  18  can also take place in the opposite direction. This is shown in  FIGS. 3A-3C . 
     The embodiment shown in  FIGS. 3A-3C  is partly identical to the one shown in the first two figures. Identical parts are provided with the same reference numerals increased by 30. The bush  36  which is connected to the rod  39  which moves inside the hollow piston rod  34  is embodied such that the device illustrated in  FIG. 2  operates in two directions. Bush  36  is received between springs  71  and  72 . The “upper part” of the piston  33  corresponds substantially to what has been described above. This means that an auxiliary valve  46  embodied as a spring plate is present which, in this example, is composed of several spring plates, as a result of which the stiffness of each shock absorber can also be adapted to the respective vehicle in a simple manner. As was the case in the preceding example, auxiliary valve  46  actuates a sleeve  45  which in turn acts on the main valve  48 . Under auxiliary valve  46 , a chamber  58  is delimited which can be connected, via apertures  38  and  41 , to the displaceable bush (dependent on whether or not these apertures are in line with one another). Via a conduit  76 , aperture  38  opens into a central inlet aperture  77  which, situated opposite aperture  78 , forms part of the part of the piston which is fixedly connected to the piston rod. When the piston moves downwards, that is to say in the direction of arrow  40 , fluid can pass into the chamber  58  via non-return valve  69  via line  53  and thus reduce pressure on sleeve  45 , as a result of which the main valve  48  opens more easily. In contrast to the above-described example, the auxiliary valve  46  does not effect complete sealing of the chamber  58 . A slot  47  is present which provides an aperture which is constantly open between chamber  58  and the part of the cylinder which is situated above the piston. This slot  47  provides a so-called constant. A corresponding slot  87  is provided on the other side and has the same function. 
     As is indicated here, the structure from  FIGS. 3A-3C  operates in two directions. This is due to the fact that conduit  76  extends also in the downward direction and can also be connected to the aperture  77 , via non-return valve  80 . When the piston is moved upwards, that is to say counter to the direction of arrow  40 , fluid can, via this non-return valve  80 , enter into conduit  76  along line  81  and subsequently, via apertures  37 ,  42 , into chamber  82  which is delimited by auxiliary valve  83 , which forces sleeve  84  upwards in order to close the other main valve  85  which operates in the opposite direction. The characteristic of both main valves  48  and  85  may differ due to the number of plate parts from which they are composed. Further details of the slot can be seen in  FIGS. 3B and 3C . 
     Due to the presence of a sealed chamber  73  under the bush  36  and the presence of a conduit  74  which connects this chamber to the part  75  which is situated above the bush, a load will be applied to rod  39 , depending on the direction of movement of the parts to which the shock absorber  31  is connected. When the actuating rod  39  is connected to a sensor (not shown), this information can be used in a simple manner to adjust the shock absorber. By means of the structure illustrated in  FIGS. 3A-3C , it is possible to change the shock absorber characteristic considerably by displacing the bush  36 . Thus, it is possible to produce an outwardly hard damping and an inwardly soft damping or the reverse. If the rod  39  is connected to an electrical control mechanism which reacts, for example, to an acceleration sensor mounted in the vehicle, it is possible to achieve damping tailored to the circumstances without having to fear excess due to phase-shift. In addition, due to the embodiment of the bush  36  and more particularly the positioning of the various abovementioned apertures, hard inward damping and soft outward damping or soft inward damping and hard outward damping are always present in combination. 
     Due to the presence of the slots  47  and  87  acting as constants, no on/off situation will occur when a fluid flow occurs in, for example, chamber  58 , as was the case with the above-described example. If the fluid flow is relatively small, the constant  47  will be able to discharge the fluid without a significant increase in pressure occurring. If the fluid flow is relatively large, auxiliary valve  46  will be lifted off its seat and the above-described effect of a reduction in the pressure on the sleeve  45  occurs. By adjusting the prestress of auxiliary valve  46  and the size of the constant  47 , the damping characteristic can be determined. 
     By means of the present invention, it is possible to adjust bush  36  at a relatively low frequency, for example at a frequency of 1-2 Hz. 
     In both abovementioned exemplary embodiments, the pressure on the main valve is reduced when filling the chamber which acts on the auxiliary valve as a result of the fact that the load applied to the main valve by the auxiliary valve is reduced as a result of the fluid pressure applied to the auxiliary valve. By adjusting the bush or slide  6 ,  36  and more particularly the apertures thereof to the chamber of the auxiliary valve, the damping characteristic can be influenced. With the embodiment illustrated in  FIG. 3 , the inward and outward damping are then set simultaneously, in which case an asymmetrical control characteristic can be achieved by means of the position of the sealing body  87  and the slot  88  in combination with the apertures  89 ,  90  and the body  91 . 
     A further variant of the invention is illustrated in  FIG. 4 . This shows a cylinder part  102  in which a piston which is denoted overall by reference numeral  103  moves up and down. The piston rod  104  is again hollow and wiring  101  is fitted on the inside for operating a coil  140  by means of which a displaceable bush  106  can be actuated. The construction of the main valves and auxiliary valves in this case substantially corresponds to that which has been shown in  FIG. 3 . In contrast to the embodiment from  FIG. 3 , the bush is not provided with the central sealing body  87 . Fluid which enters conduit  116  can flow unhindered to one of the chambers below the auxiliary valves. A compensation conduit  112  is present, as a result of which the pressure above and below the bush  106  is equal, so that the operation thereof is not effected by differences in pressure. With this embodiment, when the respective opposite aperture of the piston part is opened further, the other aperture will close, by contrast, due to the positioning of the sealing bodies  118  and  119 . As a result thereof, the controlled variable on the non-controlled side is inverted, as a result of which a direction sensor, as is used with prior art shock absorbers, is obsolete with this concept. The operation of the main valves, auxiliary valves and non-return valves is substantially as has been described with reference to  FIGS. 3 and 2 . 
       FIG. 5  illustrates a further variant of the invention. In this case, only the piston  133  is illustrated, provided with a bush  136  actuated by a coil  140 . The apertures or conduits  149 ,  150  situated opposite the bush are, via auxiliary conduits  152 ,  151 , connected to the main valves  148 ,  185  which also function as non-return valve. This application is particularly suitable for heavy shock absorbers. 
     Upon reading the above, those skilled in the art will immediately be able to think of variants which are covered by the scope of the attached claims and which are obvious after having read the above.