JP4898623B2 - Valve device - Google Patents

Description

  The present invention relates to a valve device, and more particularly to, for example, an improvement of a valve device suitable for implementation in a hydraulic shock absorber that is disposed between a floor and a ceiling of each floor of a building and is used as a vibration damper.

  For example, various proposals have conventionally been made as hydraulic shock absorbers that are arranged between floors and ceilings of each floor of a building and are used as vibration dampers. Further, it is disclosed that the damping force generated depending on the sliding position of the piston body in the cylinder body forming the hydraulic shock absorber can be adjusted in level.

  That is, in the hydraulic shock absorber disclosed in Patent Document 1, when the piston body that also forms the hydraulic shock absorber slides within the cylinder body that forms the hydraulic shock absorber, the cylinder body is defined by the piston body. A pair of oil chambers sandwiching the piston body communicate with each other via a damping valve disposed in the piston body, and a predetermined damping force is generated by the damping valve.

  On the other hand, in the hydraulic shock absorber disclosed in Patent Document 1, both the oil chambers in the cylinder body of the hydraulic shock absorber can communicate with each other via a valve device disposed outside the cylinder body. The operation of is realized by the operation of a hydraulic shock absorber.

  That is, first, the valve device is disposed in a bypass path that communicates both the oil chambers in the cylinder body of the hydraulic shock absorber outside the cylinder body, and opens and closes the bypass path when operating.

  In this valve device, the bypass path is formed by a valve mount connected to the cylinder body and a spool as a control valve slidably accommodated in the valve mount.

  Further, the valve mount is integrally connected to the cylinder body in the hydraulic shock absorber, and the spool is connected to the rod body side which is connected to the piston body in the cylinder body and can be projected and retracted with respect to the cylinder body. .

  In addition, in the hydraulic shock absorber, when the piston body is in the vicinity of the central portion in the cylinder body, the bypass passage is closed by a spool in the vicinity of the central portion in the valve mount, and the piston body is in the vicinity of the central portion in the cylinder body. When released from the center, the spool is released from the vicinity of the central portion in the valve mount.

  Therefore, in the valve device disclosed in Patent Document 1, when the piston body slides near the center in the cylinder body in the hydraulic shock absorber, the spool keeps the bypass path closed, and the cylinder Both oil chambers in the body are communicated with each other via a damping valve disposed on the piston body, so that a high damping force generation state is realized.

In this valve device, when the piston body in the hydraulic shock absorber slides out of the vicinity of the central portion in the cylinder body, the bypass path is maintained in an open state, and both oil chambers in the cylinder body are It communicates through this open bypass path, and so-called a low damping force generation state is realized.
Japanese Patent Laid-Open No. 2006-161842 (see FIGS. 1, 2 and 4)

  However, in the valve device disclosed in Patent Document 1 described above, there is no particular problem in that it is possible to adjust the level of the generated damping force depending on the expansion / contraction position of the hydraulic shock absorber. It may be pointed out that there is a minor defect in the realization.

  In other words, including the hydraulic shock absorber disclosed in Patent Document 1 described above, when a hydraulic shock absorber of a position-dependent type is used as a vibration damper in a building, the hydraulic shock absorber itself Therefore, it is important to have a so-called margin for the expansion / contraction stroke.

  Therefore, in the hydraulic shock absorber disclosed in Patent Document 1 described above, the same stroke amount as that of the hydraulic shock absorber is guaranteed for the operation of the valve device, that is, the sliding stroke of the spool as the control valve. It needs to be done.

  As a result, in the valve device disclosed in Patent Document 1 described above, for example, when the spool constituting the valve device is lengthened, the workability of the spool is likely to deteriorate and it is difficult to maintain accuracy. In addition, there is a problem that the valve device itself is easily lengthened and difficult to be compacted, and when the hydraulic shock absorber is, for example, a damping damper in a building, its installation property is reduced. There is also a problem that becomes easier.

  The present invention has been developed in view of the above-described present situation, and the object of the present invention is to make it possible to perform a predetermined function while improving the installability, and to make a general use in a hydraulic shock absorber using the same. It is an object of the present invention to provide a valve device that is optimal for expecting improvement in performance.

To achieve the above object, the constitution of the valve apparatus according to the present invention, basically, the bypass causes both an oil chamber defined by the piston body to the cylinder body in the hydraulic shock absorber communicates with the cylinder extrapyramidal When the other control valve which allows the opening and closing of the other direction in the one control valve and the bypass passage that allows one direction of opening and closing the respectively disposed in the valve mount the bypass passage to form a bypass path An input means for individually opening the two control valves to open the valve, and the control valve opens and closes the bypass passage, and an urging force for energizing the valve body from the rear side. and a spring, the bypass said input means is opened operate the control valve during sliding of the piston member in the cylinder body in the hydraulic shock absorber In the valve device in which allow arresting further opening operation for the control valve which opens the bypass passage with opening the said input means placed along the axial direction to the sliding direction of the piston body in the hydraulic shock absorber a guide rod which is held in the valve mount while being held at both ends of the guide rod and an input portion of each side opposite to the control valve, the input portion of the each side to the control valve a push member facing, is arranged behind the side of the push member and a biasing means for biasing the push member in the forward direction, the guide rod of the cylinder body in the hydraulic shock absorber the piston above base end body tip is continuously provided is connected to the rod member to project into the cylinder outside, energize the push member Biasing force of the energizing means and over the resultant force of the frictional force at the time of actuation of the spring force and the control valve of the biasing spring in the control valve.

  Therefore, in the present invention, the input means for inputting the thrust for operating the control valve disposed in the bypass passage that enables communication between both oil chambers in the hydraulic shock absorber outside the cylinder body is provided in the cylinder body. Since the control valve is actuated when the piston body slides to open the bypass passage, the operation of the control valve that has opened the bypass passage can be further stopped by the actuation, so that the hydraulic pressure buffer to which the input means is connected Even if the so-called expansion / contraction stroke in the vessel exceeds the operation stroke in the control valve, that is, the effective stroke, the input means does not input a thrust force for further operating the control valve.

  As a result, the effective stroke, which is the operation stroke of the control valve, can be set independently of the expansion / contraction stroke of the hydraulic shock absorber, and the operation stroke of the control valve only needs to be slightly increased in consideration of the so-called safety factor. When the valve is provided on a valve mount connected to the cylinder body, the valve mount can be made compact.

  By the way, in the hydraulic shock absorber, when the piston body that is slidably accommodated in the cylinder body and defines both the oil chambers that form a pair in the cylinder body has a damping valve that allows communication between both oil chambers When the bypass path outside the cylinder body is closed, a high damping force is generated by each damping valve during an expansion / contraction operation in which the rod body protrudes and retracts with respect to the cylinder body.

  In the hydraulic shock absorber, the stroke of the rod body relative to the cylinder body is large. Therefore, when there is input from the input means to the control valve, the bypass path is opened and both oil chambers in the cylinder body are opened. It is communicated via.

  As a result, the damping valve of the piston body that was maintained in a high damping force generation state until the bypass passage was opened by the operation of the control valve is the same as that until the bypass passage was opened by the operation of the control valve. The generated damping force is reduced.

  Then, the piston body reverses in the cylinder body and shifts to the reverse stroke. Therefore, when the control valve cancels its operation, the bypass path is closed and a high damping force is generated by the damping valve of the piston body. Is done.

  The present invention will be described below on the basis of the illustrated embodiment. The valve device according to the present invention is embodied in a hydraulic shock absorber that is cylindrical and double-rod shaped in the illustrated case. The hydraulic shock absorber is, for example, a vibration damper disposed between the floor and ceiling of each floor of the building.

  The hydraulic shock absorber shown in the figure is a cylinder body 1 and both oil chambers that are paired so as to have the same cross-sectional area in the cylinder body 1 while being slidably received in the cylinder body 1. That is, the piston body 2 that defines one oil chamber R1 that is upper in the figure and the other oil chamber R2 that is lower in the figure, and each oil chamber while its base end is connected to the piston body 2 The rod body 3 that is inserted through the shaft cores of R1 and R2 and projects the tip from the closed end of the cylinder body 1 to the outside, that is, the one rod body 31 that is the upper side in the drawing with the same cross-sectional area. It has the other rod body 32 which becomes the inside downward.

  In this hydraulic shock absorber, the piston body 2 has damping valves 21 and 22 that allow communication between both the oil chambers R1 and R2, and the cylinder body 1 includes control valves 5 and 6 described later. The valve mount 4 that enables the arrangement of the valve body 4 is integrally connected, and the valve mount 4 has a plate portion 41 that is connected to the cylinder body 1 while having only a port (not shown). And a housing part 42 connected to the plate part 41 and having control valves 5 and 6 and check valves 7 and 8.

  By the way, the cylinder body 1 is a so-called cylindrical body because the hydraulic shock absorber is a double rod type. In the drawing, a sub cylinder body 11 having the same diameter as the cylinder body 1 is provided at the lower end side in the drawing. Are connected in a coaxial manner, and the tip end side which is the lower end side in the drawing of the other rod body 32 is made conductive in the sub cylinder body 11 so that the lower end side of the other rod body 32 interferes with a so-called other part. The sub-cylinder body 11 has a bracket 12 that allows the hydraulic shock absorber to be attached.

  The piston body 2 itself is a damping valve that allows communication between both oil chambers R1 and R2 defined in the cylinder body 1, that is, a damping valve 21 that is used for the expansion side, and a damping valve that is used for the compression side. The valve 22 is arranged in parallel.

  At this time, the damping valves 21 and 22 are set so as to open when the upstream pressure exceeds the cracking pressure, and the cracking pressure is arbitrarily set.

  The rod body 3 has a bracket 33 at the tip of one of the rod bodies 31 that is upper in the drawing, and the hydraulic shock absorber can be attached using the bracket 33.

  Therefore, in this hydraulic shock absorber, attachment to a desired location using the brackets 12 and 33, that is, installation is possible, and operation at the installation location, that is, so-called expansion and contraction. Operation is enabled.

  In this hydraulic shock absorber, if a bypass path, which will be described later, is ignored, assuming that the piston body 2 rises in the cylinder body 1 in the drawing, for example, when the expansion side is operating, one oil chamber R1 communicates with the other oil chamber R2 via the damping valve 21. At this time, a damping force having a predetermined magnitude is generated by the damping valve 21.

  Similarly, in this hydraulic shock absorber, assuming that the piston body 2 descends in the drawing in the cylinder body 1 in the drawing, for example, when operating on the pressure side, the other oil chamber R2 is connected via the damping valve 22 to one side. At this time, a damping force of a predetermined magnitude is generated by the damping valve 22.

  Next, in this hydraulic shock absorber, a bypass path (not shown) that bypasses the damping valves 21 and 22 provided in the piston body 2 and communicates both the oil chambers R1 and R2 outside the cylinder body 1. It has.

  At this time, so-called both ends of the bypass path communicate with the oil chambers R1 and R2 in the cylinder body 1 at portions that serve as so-called stroke end regions in the oil chambers R1 and R2.

  That is, when the piston body 2 slides in the cylinder body 1 with a large stroke exceeding the so-called neutral region and approaches the end of the cylinder body 1, the cylinder body 1 is opened. The opened opening is not closed and the communication of the oil chambers R1, R2 to the bypass path is not hindered.

  On the other hand, in the present invention, the valve device includes a bypass path that allows communication between the oil chambers R1 and R2 outside the cylinder body 1 and an input of thrust from the outside disposed in the bypass path. Control valves 5 and 6 that move to open the bypass path, check valves 7 and 8 that rectify the flow of hydraulic oil in the bypass path with respect to the control valves 5 and 6, and inputs that input thrust to the control valves 5 and 6 Means 9.

  First, the bypass passage is formed in the valve mount 4 integrally connected to the cylinder body 1, that is, in the illustrated case, in the plate portion 41 and the housing portion 42. Control valves 5 and 6 arranged in parallel so as to allow communication in opposite directions between the oil chambers R1 and R2, and a check valve 7 for controlling the flow direction of hydraulic oil in the bypass passage, that is, for rectifying , 8.

  At this time, in view of the original function of the bypass path, the valve mount 4 is held by the cylinder body 1 regardless of whether it is formed on the valve mount 4. In that case, it is preferable.

  That is, as will be described later, in the valve device of the present invention, the control valves 5 and 6 disposed in the bypass passage are via the input means 9 but depend on the expansion / contraction position of the hydraulic shock absorber. Therefore, at least in the valve mount 4 having the control valves 5 and 6, this may be imitated by a part of the cylinder body 1. The valve mount 4 is preferably provided integrally with the cylinder body 1 and held by the cylinder body 1.

  Next, the control valves 5 and 6 are opened by an input from the input means 9 following the movement of the rod body 3 with respect to the cylinder body 1 as shown in the figure. Allow communication to the room.

  That is, for example, the control valve 5 is switched to an open state by an input from the input means 9 when the hydraulic shock absorber in which one rod body 31 is immersed in the cylinder body 1 is contracted, and the other The oil chamber R2 communicates with one of the oil chambers R1 through the opened control valve 5. At this time, the control valve 6 is maintained in a shut-off state in its own state because the check valve 7 operates. To that extent, the bypass is closed.

  Even in the control valve 6, one rod body 31 protrudes from the cylinder body 1, so that it is switched to the open state by the input from the input means 9 during the extension side operation, and one oil chamber R1 is The control valve 5 communicates with the other oil chamber R2 via the opened control valve 6, and at this time, the control valve 5 is shut off in its own state because the check valve 8 is operated in the same manner as described above. It is maintained in the state and the bypass is closed as long as it is.

  As for the check valves 7 and 8, as described above, for example, when the control valve 5 is opened by the contraction of the hydraulic shock absorber in which one rod body 31 is immersed in the cylinder body 1, When the check valve 7 prevents the hydraulic oil in the oil chamber R2 from flowing into the control valve 6 and the control valve 5 comes back, that is, the rod body 31 extends from the inside of the cylinder body 1. When the hydraulic oil flowing out from the oil chamber R1 in the cylinder body 1 flows into the control valve 5 that has not yet been shut off, the check valve 8 prevents this, and the control valve 8 5 functions to maintain a predetermined closed state, and only the damping valve 21 of the piston body 2 in the hydraulic shock absorber is operated, so that a predetermined amount of damping is achieved. There is generated.

  Then, when the control valve 6 is opened by the extension of the hydraulic shock absorber in which one rod body 31 projects from the cylinder body 1, the hydraulic oil in the oil chamber R 1 in the cylinder body 1 flows into the control valve 5. When the check valve 8 prevents the control valve 6 from returning, that is, by reversing the contraction in which one rod body 31 is immersed in the cylinder body 1, the oil flows out from the oil chamber R2 in the cylinder body 1. The check valve 7 functions to prevent the hydraulic oil from flowing into the control valve 6 that has not yet been shut off, and to prevent the check valve 7 from being in a predetermined closed state. Only the damping valve 22 of the piston body 2 in the hydraulic shock absorber operates, and a damping force having a predetermined magnitude is generated.

  From the above, according to the present invention, it is of course possible to adjust the level of the damping force generated by the hydraulic shock absorber by opening and closing the bypass path by the control valves 5 and 6. Also, due to the cooperation of the check valves 7 and 8, a displacement characteristic of the damping force as shown in FIG. 2 is obtained.

  Here, as for the control valves 5 and 6, as shown in the figure, the control valves 5 and 6 include input shafts 51 and 61, valve bodies 52 and 62, base shafts 53 and 63, and biasing springs 54 and 64. It is said to have.

  That is, first, the input shafts 51 and 61 are configured to input the thrust from the opposing input means 9 to the tip, and the axial direction is the same as that of the rod body 3 described above.

The input shafts 51 and 61 are placed in the atmosphere with their tip portions that face the input means 9 projecting from the housing portion 42 of the valve mount 4 and are not shown in detail. , has to permit the length adjustment of the axial length at the tip, the adjustment of the distance to the input means 9, i.e., allowing the length adjustment of the dead zone the stroke L1, L2 to be described later.

  In addition, in the place shown in the figure, the input shafts 51 and 61 have kerfs 51a and 61a as oil passages that realize flow rate control according to displacement in spool portions that are forward portions of valve bodies 52 and 62, which will be described later. One or more are formed.

  Next, the valve bodies 52 and 62 are connected in series to the base ends of the input shafts 51 and 61, that is, in the illustrated case, the valve bodies 52 and 62 are integrally connected to each other so that the bypass passages are opened when the input shafts 51 and 61 are retracted. As shown in the figure, it is made of a poppet, and therefore effectively prevents leakage of hydraulic oil in the bypass passage as compared with the case where the valve bodies 52 and 62 are made of a spool.

  And since the said groove 51a, 61a is formed in the upstream of the poppet which is the valve bodies 52, 62, according to a stroke by using the flow of the hydraulic oil through this groove 51a, 61a. 2 can be controlled, for example, the waveform in the cylinder region indicated by the symbol X in the characteristic diagram of FIG. 2 can be controlled, and even if this waveform control is not required, the valve bodies 52 and 62 can be controlled. So-called shocks can be alleviated without sudden opening and closing.

  In addition, about said valve body 52,62, this may consist of a spool, and when it consists of a spool, it is good also as making a poppet in series with this.

  The base shafts 53 and 63 are connected in series to the valve bodies 52 and 62, that is, in the drawing, the shaft diameters are the same as the input shafts 51 and 61 while being integrally connected to the rear ends of the valve bodies 52 and 62. Thus, the rear ends are placed in the atmosphere, and the rear ends of the base shafts 53 and 63 are placed in the atmosphere while the tips of the input shafts 51 and 61 are placed in the atmosphere. The forward movement state is maintained only by the spring force of the biasing springs 54 and 64, that is, the bypass passage is closed.

  Although the urging springs 54 and 64 are coil springs as shown in the drawing, the urging forces in the respective urging springs 54 and 64 are not required to be so-called identity unless they are extremely small.

  The urging springs 54 and 64 contract to allow the base shafts 53 and 63 to retreat, that is, the valve bodies 52 and 62 retreat when the thrust from the input means 9 is input. The flow of hydraulic oil in the bypass passage through the valve bodies 52 and 62 is allowed.

  By the way, regarding the spring force of the biasing springs 54 and 64, as described above, in the control valves 5 and 6 of the present invention, the input shaft 51 that sandwiches the poppets that are the valve bodies 52 and 62. , 61 and the base shafts 53, 63 have the same so-called axial force.

  Therefore, when the valve bodies 52 and 62 are seated on a so-called valve seat portion and the bypass path is maintained in the closed state, the biasing spring having a spring force superior to the friction when the control valves 5 and 6 are operated. Therefore, when the biasing springs 54 and 64 are coil springs, so-called light coil springs are sufficient.

  On the other hand, the input means 9 is basically formed so as to be synchronized with the movement of the rod body 3 described above and is paired so as to correspond to the control valves 5 and 6. The connecting member 91 connected to the upper rod body 31 in the figure, and the valve mount while keeping the axial direction along the sliding direction of the piston body 2 in the hydraulic shock absorber, that is, along the axial direction of the rod body 3 4 is connected to a guide rod 92 held by the housing part 42.

  Here, as to the holding state of the guide rod 92 to the housing part 42, according to the configuration of the input means 9, the guide rod 92 is movably held by the housing part 42, that is, slidable.

  In the illustrated embodiment, the connecting member 91 is bent so as to exhibit a laterally wide-angle U-shaped cross section in a posture surrounding the housing portion 42 and the pair of input means 9 in the so-called inner valve mount 4. In addition, an adjusting portion 91a is provided at a so-called intermediate portion, and dead zone strokes L1 and L2, which will be described later, that is, an interval between the input means 9 and the control valves 5 and 6 can be adjusted.

  Next, while the guide rod 92 is movably interposed from the housing portion 42 to the tip portions that are both ends projecting outward in the axial direction of the rod body 3, the guide rod 92 moves out from the tip portion in the axial direction of the guide rod 92. It has an input (not shown) that is allowed, i.e., allowed to retract.

The input portion is disposed at the distal end portion of the guide rod 92 so as to be movable and selectively faces the control valves 5 and 6, and is disposed behind the push member 93. An urging spring 94 as urging means for urging the push member 93 in the forward direction is provided, and a guide rod 92 is connected to the connecting member 91.

  At this time, the push member 93 is opposed to the tips of the input shafts 51 and 61 in the control valves 5 and 6 with a gap, and this gap is set to the dead zone strokes L1 and L2.

The push member 93 is carried by a stepped portion (not shown) formed on the guide rod 92 and is pressed against the stepped portion by a spring force as a biasing force of the biasing spring 94.

  Therefore, in this input means 9, for example, when one rod body 31 is immersed in the cylinder body 1, until the rod body 31 is immersed in the cylinder body 1 more than the dead zone stroke L1 described above. The push member 93 does not interfere with the tip of the input shaft 51 in the control valve 5, so that the control valve 5 does not open.

  When the stroke in which the rod body 31 is immersed in the cylinder body 1 is equal to or greater than the dead zone stroke L1, the push member 93 comes into contact with the tip of the input shaft 51 in the control valve 5, and this input shaft 51 is connected to the valve mount 4. The control valve 5 is actuated to be opened by being immersed in the housing part 42.

  In the above operation, the push member 93 on the opposite side in the input means 9 operates similarly to the input shaft 61 in the control valve 6 even when the other rod body 32 is immersed in the cylinder body 1. Therefore, the control valve 6 operates in the same manner as the control valve 5 described above.

  The urging spring 94 is disposed between the push member 93 and the spring receiver 95 screwed on the guide rod 92. The spring receiver 95 is shown in FIG. The threaded position on the strip shaft 92a can be moved in the axial direction of the guide rod 92, the length of the biasing spring 94 can be adjusted, and the initial load of the biasing spring 94 can be adjusted. I have to.

  By the way, in this input means 9, the push member 93 is interposed in the stepped portion of the guide rod 92, and comes out of the guide rod 92 in the axial direction so as to overcome the biasing spring 94. Movement is allowed.

  That is, in this input means 9, the spring force of the biasing spring 94 is the resultant force of the spring force of the biasing springs 54 and 64 in the control valves 5 and 6 and the frictional force when the control valves 5 and 6 are operated. Therefore, when the push member 93 moves forward and comes into contact with the input shafts 51 and 52 of the control valves 5 and 6, the input shafts 51 and 61 are connected to the spring force of the biasing springs 54 and 64. Then, it overcomes the resultant force with the frictional force at the time of operation of the control valves 5 and 6, and retracts.

  At this time, since the push member 93 is urged by the urging spring 94, the push member 93 apparently moves forward together with the guide rod 92 and operates in the same manner as the rod body 3.

  However, when the poppets 52 and 62 are mechanically prevented from moving backward in the control valves 5 and 6, or the input shafts 51 and 61 are completely immersed in the housing portion 42 of the valve mount 4. Then, the retraction of the input shafts 51 and 61 is stopped, so that the subsequent movement of the push member 93, that is, the forward movement is also prevented, and the biasing spring 94 is contracted.

  In other words, the input means 9 opens the control valves 5 and 6 by opening the control valves 5 and 6 when the rod body 3 is inserted into the cylinder body 1 in the hydraulic shock absorber, and opens the control valves 5 and 6 that open the bypass path. Further, the input of the thrust force that causes the opening operation is stopped.

  When the push member 93 continues to be pressed against the housing portion 42 even after the operation stroke of the control valves 5 and 6 is stopped, it is as if the push member 93 overcomes the spring force of the biasing spring 94 and moves backward. The situation appears, and at this time, the rod body 3 in the hydraulic shock absorber can be further expanded and contracted.

  As described above, in the valve device of the present invention, when the expansion / contraction amount exceeds the dead zone strokes L1 and L2 during the so-called expansion / contraction operation in which the rod body 3 is projected and retracted with respect to the cylinder body 1, so to speak. The corresponding control valves 5 and 6 are opened to switch the bypass path to the communication state.

  Therefore, according to this, in the valve device of the present invention, when the dead zone strokes L1 and L2 are the same, the hydraulic shock absorber is in a so-called neutral state.

  That is, when the hydraulic shock absorber is installed at an arbitrary place, so-called installation intervals at the installation location vary, and therefore, in the hydraulic shock absorber, the piston body 2 is positioned at the complete central portion in the cylinder body 1. Even if it is difficult to determine, that is, to make the neutral state practically, the so-called neutral of the piston body 2 with respect to the cylinder body 1 is obtained by adjusting the dead zone strokes L1 and L2 to be the same. It becomes possible to reveal the state.

  At this time, even if the piston body 2 is not in a completely neutral state in the cylinder body 1, in most cases, the deviation will not be unnecessarily large, which will be larger than the so-called tolerance. Therefore, it can be said that there is no problem even if it is assumed that the hydraulic shock absorber is in a neutral state by adjusting the dead zone strokes L1 and L2 to be the same.

  In view of the above, according to the present invention, when installing the hydraulic shock absorber, it is possible to reliably show the neutral state in the valve device while visually confirming the state of the conventional hydraulic shock absorber. In the installation, the so-called neutral state is not easily displayed. Therefore, it is possible to realize a quick installation work as compared with the case where the installation of the hydraulic shock absorber is troublesome.

  In the above description, the case where the hydraulic shock absorber equipped with the valve device according to the present invention is used as a vibration damper in a building is taken as an example. For example, it may be used for vibration control of railway vehicles and equipment other than objects.

  In the above description, the present invention is embodied in a double rod type hydraulic shock absorber. However, from the point of view of the present invention, the present invention is embodied in a single rod type hydraulic shock absorber. Furthermore, if it is a shock absorber using a fluid other than gas, which is a so-called non-shrinkable fluid, it can be realized.

  Further, as described above, as shown in FIG. 1, the control valves 5 and 6 are arranged in a posture parallel to the hydraulic shock absorber in the left-right direction in the drawing to reduce the depth dimension. However, although not shown, the parallel control valves 5 and 6 may be arranged so as to overlap the hydraulic shock absorber to reduce the width dimension.

  Further, in the above description, the hydraulic shock absorber equipped with the valve device according to the present invention has been described as an example in which the valve mount 4 is integrally held by the cylinder body 1. Even if the valve mount 4 is separated from the cylinder body 1, a neutral state in the hydraulic shock absorber can be realized.

  That is, regarding the installation of the hydraulic shock absorber at a predetermined position, the cylinder body 1 is first installed at the installation site in a state where it can be said that the cylinder body 1 is roughly viewed and is in a neutral state, and is separated from the cylinder body 1 after the dredging. If the valve mount 4 is moved and the dead zone strokes L1 and L2 are the same on the left and right sides, a neutral state in the hydraulic shock absorber can be realized.

  In the valve device according to the present invention, when the control valves 5 and 6 are embodied, the control valves 5 and 6 are not formed uniaxially but formed biaxially. Or, considering the case where it is installed in the cylinder body 1, it is easy to prevent the valve mount 4 from being miniaturized, or avoid the inconvenience that the equipment in the cylinder body 1 tends to be disadvantageous. This is advantageous in that it can be done.

  However, from the point of view of the present invention, although not shown, the control valves 5 and 6 may be embodied in a so-called uniaxial arrangement in series.

It is a principle figure showing a hydraulic shock absorber provided with a valve device by one embodiment of this invention. It is a figure which shows the displacement characteristic of the damping force by the damping valve which a piston body has.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Cylinder body 2 Piston body 3 Rod body 4 Valve mount 5,6 Control valve 9 Input means 21,22 Damping valve 31 One rod body 32 The other rod body 51,61 Input shaft 52,62 Valve body 53,63 Base shaft 54 , 64 Energizing spring 92 Guide rod 93 Push member forming the input portion 94 Energizing springs as energizing means R1, R2 Oil chamber

Claims (6)

A bypass passage for the oil chamber both being defined by the piston body to the cylinder body in the hydraulic shock absorber communicates with the cylinder outside, respectively disposed in the valve mount unidirectional in the bypass passage to form a bypass path has the other control valve which allows the opening and closing of the other direction in the one control valve and the bypass passage that enables opening and closing, and input means for opening operation by entering the thrust individually to the two control valves , a valve body in which the control valve to open and close the bypass passage, and a biasing spring for biasing the valve body from the rear side, the piston of said input means in the cylinder body in the hydraulic shock absorber a further opening when sliding on by opening operation of the control valve to said control valve by opening the bypass passage causes the opening the bypass passage In the valve device in which allow the stopping of operation,
A guide rod which the input means is held in the axial direction in the valve mount while along the sliding direction of the piston body in the hydraulic shock absorber, is held at both ends of the guide rod facing the control valve and an input portion of each side, and a push member which input of the each side is opposed to the control valve, it is arranged behind the side of the push member biasing the push member in the forward direction biasing of Power means ,
The guide rod is connected to a rod member having a base end to the piston of the cylinder body is to project the tip is continuously provided on the cylinder outside in the hydraulic shock absorber,
The valve device according to claim 1, wherein the urging force of the urging means for urging the push member is superior to a resultant force of a spring force of the urging spring in the control valve and a frictional force when the control valve is operated . And it has a damping valve in which the hydraulic shock absorber to allow communication of both oil chambers in the piston body slidably accommodated within the body the cylinder, the cross-sectional area in the same by connecting the proximal end to the piston member valve device according tip by inserting the shaft core portion of both the oil chambers to claim 1 comprising a rod of both the one and the other to protrude above the cylinder outside while. Together with the bypass passage is formed in the valve mount provided continuously to the cylinder body in the hydraulic shock absorber, the control valve is held in the valve mount, the thrust from the input means said control valve faces an input shaft for retraction by the input to the front end, while being connected to the proximal end of the input shaft and the valve body for opening the bypass passage at the time of retraction, volume communicating with the atmosphere while being continuously to the valve body The valve device according to claim 1 , further comprising a base shaft defining a chamber. Valve device according to claim 1, claim 2 or claim 3 in which the distal end portion of the input shaft in the control valve opposite to the input means is to allow the length adjustment of the axial length. The valve device according to claim 1, 2, 3, or 4, wherein the valve body in the control valve has a poppet or a spool for opening and closing the bypass passage . The said bypass path is closed by the said control valve when the said piston body exists in the center part vicinity of the said cylinder body in the said hydraulic shock absorber, The claim 3, Claim 3, Claim 4 or Claim 5. The valve device according to 5.

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