JP4921313B2 - 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 further relief valve device in which allow the stopping of operation, the base end to the piston of the cylinder body is continuously provided in said input means said hydraulic shock absorber to said control valve and opening the bypass passage with opening the a guide pipe for retractable penetrates the valve mount while along the which the tip is in the sliding direction of the piston body in a linked the hydraulic shock absorber the rod member to project into the cylinder outside the body to retractably in the guide pipe a guide rod which moves in synchronism with the sliding of the piston member is inserted, arranged has been the other in the bypass passage between the other end of the guide pipe to close and the other end of the guide rod to and the other input portion facing the control valve, the to close to the one end of the guide rod Gaidopa Disposed between the other end of the flop and a one input section opposite to said one control valve in the bypass passage, and a push member which the input portion of the each side is opposed to the control valve, Biasing means disposed behind the push member and biasing the push member in the forward direction, and the biasing force of the biasing means for biasing the push member is the biasing force in the control valve. Assume that the spring force of the spring is better .

  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 the 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, when the piston body reverses in the cylinder body and shifts to the reverse stroke, and when the control valve releases its operation, the bypass passage is closed and a high damping force is generated by the damping valve of the piston body. The state is guaranteed.

  In the present invention, since the guide pipe and the guide rod for disposing the input portion constituting the input means are disposed so as to penetrate the housing portion which is the valve mount, the guide pipe and the guide rod are Compared to the case where the valve device is disposed outside the valve mount, an unnecessarily large size of the valve device can be avoided, and the valve device can be made compact.

  In the following, the present invention will be described based on the illustrated embodiment. However, the valve device according to the present invention is embodied in a hydraulic shock absorber having a cylindrical shape and a double rod shape. The hydraulic shock absorber is, for example, a vibration damper disposed between a floor and a ceiling of each floor of a building.

  The hydraulic shock absorber shown in FIG. 1 includes both a cylinder body 1 and a pair of cylinders 1 having the same cross-sectional area while being slidably received in the cylinder body 1. An oil chamber, that is, a 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 one end connected to the piston body 2 A rod body 3 that passes through the shaft cores of the oil chambers R1 and R2 and projects the tip from the closed end of the cylinder body 1 to the outside, that is, one rod body 31 that has the same cross-sectional area and is upward in the drawing. And the other rod body 32 on the lower side in the figure.

  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 is disposed integrally with the plate portion 41. The valve mount 4 includes a plate portion 41 that is connected to the cylinder body 1 while having only a port (not shown). The housing portion 42 is connected to the plate portion 41 and includes 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 figure, a sub-cylinder body 11 having the same diameter as the cylinder body 1 is provided on the lower end side in the drawing. A bracket that is connected coaxially, and that the leading end side, which is the lower end side in the drawing, of the other rod body 32 is electrically connected to the sub-cylinder body 11 so that the sub-cylinder body 11 can attach the hydraulic shock absorber so-called. 12.

  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 figure. Therefore, in this hydraulic shock absorber, the bracket 33 and the bracket 12 described above are used. Installation at a desired location is possible, and so-called telescopic operation at the installation location is possible.

  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, and 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. A damping force of a predetermined magnitude is generated by the damping valve 22 in communication with the oil chamber R1.

  Next, in this hydraulic shock absorber, both the oil chambers R1 and R2 are communicated outside the cylinder body 1 by bypassing the damping valves 21 and 22 provided in the piston body 2, and the valve device according to the present invention is provided. A bypass path (not shown) is provided.

  The so-called both ends of the bypass path are in communication with the oil chambers R1 and R2 in the cylinder body 1 at portions serving 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 a so-called neutral region and reaches the vicinity of 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 passage that allows communication between the oil chambers R1 and R2 outside the cylinder body 1 as described above, and an external thrust that is disposed in the bypass passage. Control valves 5 and 6 that move by input 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 input thrust to the control valves 5 and 6 And input means 9 for receiving.

  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 are arranged.

  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 or not. That 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. It is allowed to communicate with the room.

  That is, for example, in one control valve 5, one side of the rod body 31 in the cylinder body 1 is switched to the open state by the input from the input means 9 during the pressure side operation of the hydraulic shock absorber. The other oil chamber R2 communicates with the one oil chamber R1 via the opened one control valve 5, and at this time, the other control valve 6 has a place where the check valve 7 operates, In the state, it is maintained in the shut-off state, and as long as the bypass path is closed.

  Even in the other 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 the one oil chamber R1 communicates with the other oil chamber R2 via the opened other control valve 6, and at this time, one control valve 5 has a place where the check valve 8 operates in the same manner as described above. In its own state, it is maintained in a shut-off state, and as long as the bypass path is closed.

  As for the check valves 7 and 8, as described above, for example, when one control valve 5 is opened by the pressure side operation of the hydraulic shock absorber in which one rod body 31 is immersed in the cylinder body 1, the oil chamber When the check valve 7 prevents the hydraulic oil of R2 from flowing into the other control valve 6 and one of the control valves 5 returns to the so-called return direction, that is, the hydraulic shock absorber reverses to the extension side operation, The check valve 8 prevents this when the hydraulic oil flowing out from the chamber R1 flows into one control valve 5 that has not yet been shut off, and puts one control valve 5 in a predetermined closed state. In addition to functioning to maintain, only the damping valve 21 operates in the hydraulic shock absorber, and a damping force having a predetermined magnitude is generated.

  The hydraulic oil in the oil chamber R1 flows into the one control valve 5 when the other control valve 6 is opened by the extension side operation of the hydraulic shock absorber in which one rod body 31 projects from the cylinder body 1. When the check valve 8 prevents the other control valve 6 from returning, that is, by reversing the pressure side operation in which one rod body 31 is immersed in the cylinder body 1, the oil is discharged from the oil chamber R2. The check valve 7 functions to prevent the hydraulic oil from flowing into the other control valve 6 that has not yet been shut off, and to prevent the hydraulic oil from being in a predetermined closed state. At the same time, only the damping valve 22 operates in the hydraulic shock absorber, and a damping force having a predetermined magnitude is generated.

  In view of the above, according to the present invention, the level of the damping force generated by the hydraulic shock absorber can be adjusted by opening and closing the bypass path with the control valves 5 and 6. , 8 in cooperation with each other, a displacement characteristic of the damping force as shown in FIG. 2 is obtained.

  Here, the control valves 5 and 6 will be described. Basically, as shown in FIG. 1, the control valves 5 and 6 include input shafts 51 and 61, valve bodies 52 and 62, and base shafts 53 and 63. And urging springs 54 and 64.

  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. In addition, it is possible to adjust the length of the shaft at the tip, and to adjust the distance to the input means 9, that is, to adjust the length of the dead zone strokes L1 and L2, which will 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 one end of the input shafts 51 and 61, that is, in the illustrated state, 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, it is possible to effectively prevent leakage of hydraulic oil in the bypass passage as compared with the case where the valve bodies 52 and 62 are made of only a spool.

  And since said kerf 51a, 61a shall be formed in the upstream of the poppet which is the valve bodies 52, 62, since the flow of the hydraulic oil through this kerf 51a, 61a is utilized, a stroke 2 can be controlled, for example, the waveform in the region indicated by the symbol X in the characteristic diagram of FIG. 2 can be controlled, and even when control of this waveform is not required, the valve body 52, The so-called shock can be alleviated without the 62 being suddenly opened and closed.

  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. Since the rear ends of the input shafts 51 and 61 are also placed in the atmosphere while the rear ends of the base shafts 53 and 63 are placed in the atmosphere. 52 and 62 are maintained in the advanced state only by the spring force of biasing springs 54 and 64, which will be described later, that is, maintained in a state in which the bypass path 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.

  In the biasing springs 54 and 64, when the thrust from the input means 9 is input, the biasing springs 54 and 64 contract to allow the base shafts 53 and 63 to retract, that is, the valve bodies 52 and 62 retract. 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 follow the movement of the piston body 2 in the hydraulic shock absorber, that is, the rod body 3. A guide pipe 91 that penetrates the housing portion 42 of the valve mount 4 so as to be movable in the vertical direction in FIG.
A guide rod 92 that is inserted into the guide pipe 91 so as to be able to project and retract and moves in synchronization with the sliding of the rod body 3 that is not slidable of the piston body 2, and one end of the guide rod 92 and a guide pipe adjacent thereto. Between the other end of the guide rod 92 and the other end of the guide pipe adjacent thereto. And one input portion 93 facing one control valve 5 in the bypass path.

  At this time, the guide pipe 91 and the guide rod 92 are disposed so as to pass through the housing portion 42 that is the valve mount 4, and although not shown, the guide pipe 91 and the guide rod 92 are disposed outside the valve mount 4. Compared to the case, the tampering of the valve device can be avoided and the valve device can be made compact.

  In the input means 9, the guide rod 92 is connected at its upper end in the drawing to the rod body 3 in the hydraulic shock absorber, that is, to one rod body 31 in the drawing by the arm member 95. The rod body 3 can be synchronized with the movement of the rod body 3.

  Incidentally, for the connection of the arm member 95 to the guide rod 92, a so-called bolt 95a nut 95b structure is adopted, and it is possible to adjust the interval of dead zone strokes L1, L2 to be described later with respect to the control valves 5, 6 of the input means 9. ing.

Moreover, in this input means 9, each input part 93,94 is a push member 93a, 94a aiming at the front-end | tip of the input shaft 51,61 of the corresponding control valve 5,6, and this push member 93a, 94a. Urging springs 93b and 94b as urging means for urging the urging force from the rear side, spring receivers 93c and 94c for locking the base ends of the urging springs 93b and 94b, and the spring receivers 93c and 94c are connected to the guide rod 92. And nuts 93d and 94d that are fixed to be movable.

  At this time, in each of the input portions 93 and 94, the push members 93a and 94a are opposed to the tips of the input shafts 51 and 61 in the control valves 5 and 6 with an interval, and this interval is defined as the dead zone stroke L1, L2.

Further, in the the input means 9, biasing spring 93 b, biasing force serving spring force of 94b is better than the spring force of the biasing spring 54, 64 in the control valve 5 and 6, therefore, the push member 93a, 94a is When the control valve 5 and 6 are brought into contact with the tips of the input shafts 51 and 61 in the control valve 5, 6, the guide pipe 91 and the guide rod 92 are apparently moved together. 6, the input shafts 51, 61 are moved backward so that the poppets that are the valve bodies 52, 62 are moved away from the valve seat portion, and the bypass path is opened.

  Incidentally, in each input part 93 and 94, the spring force in each biasing spring 93b and 94b is adjusted in height by adjusting the screwing position of each nut 93d and 94d.

  Further, in the input means 9, in the input portions 93, 94, the push members 93a, 94a are welded and fixed to the guide pipe 91. The portions 93 and 94 may be locked to the guide pipe 91 with a snap ring.

  Here, the operation of the valve device according to the present invention will be described. First, in the state shown in FIG. 1, in the hydraulic shock absorber, the piston body 2 in the cylinder body 1 is in a neutral position, and one control valve 5 and one input section are provided. The dead zone stroke L1 appearing between the control valve 6 and the dead zone stroke L2 appearing between the other control valve 6 and the other input unit 94 is the same.

  Therefore, for example, when the piston body 2 is lowered in the cylinder body 1 in the hydraulic shock absorber, and thus the rod body 3 is immersed in the cylinder body 1, the guide rod 92 is interposed via the guide pipe 91. However, it descends so as to be immersed in the housing part 42 in the valve mount 4.

  At this time, since the one input portion 93 is provided between the guide rod 92 and the guide pipe 91, the one input portion 93 follows the movement of the guide rod 92 and moves together with the guide pipe 91. Until the moving stroke becomes equal to or greater than the dead zone stroke L1, one of the control valves 5 does not open, so that the bypass path is closed. Therefore, in the hydraulic shock absorber, the other oil chamber R2 is attenuated. The valve 22 communicates with one oil chamber R1.

  When the movement stroke of the guide rod 92, that is, the one input portion 93 is equal to or greater than the dead zone stroke L1, the push member 93a in the one input portion 93 contacts the tip of the input shaft 51 in the control valve 5, and the push member 93a is Since the spring force of the biasing spring 93b that biases overcomes the spring force of the biasing spring 54 in the control valve 5, the input shaft 51 moves backward as the push member 93a moves forward, and one control valve 5 opens. To do.

  At this time, since the bypass path is opened, in the hydraulic shock absorber, the other oil chamber R2 tends to communicate with the one oil chamber R1 through the opened bypass path. The high damping force that has been generated until then becomes lower.

  When the operation is continued in the hydraulic shock absorber and the lowering of the guide rod 92 is continued, it is the same as described above until the moving stroke of the one input portion 93 exceeds the operating stroke of the one control valve 5, When the operating stroke of one control valve 5 is exceeded, the forward movement of the push member 93a is prevented.

  At this time, the control valve 5 may be mechanically prevented from moving backward to prevent the push member 93a from moving forward, and the push member 93a may interfere with the housing portion 42, for example. It may be possible to prevent the forward movement.

  In addition, when the operation of the hydraulic shock absorber continues even after the control valve 5 is prevented from moving backward, there is no operation stroke in the control valve 5, and therefore the push member 93a causes the biasing spring 93b to contract. fall back.

  On the other hand, when the piston body 2 rises in the cylinder body 1 in the hydraulic shock absorber, and thus the rod body 3 protrudes from the cylinder body 1, the guide rod 92 is interposed via the guide pipe 91. The valve mount 4 rises so as to protrude from the housing part 42.

  At this time, since the other input portion 94 is provided between the guide rod 92 and the guide pipe 91, the other input portion 94 moves along with the guide pipe 91 following the movement of the guide rod 92. Until the moving stroke becomes equal to or greater than the dead zone stroke L2, the other control valve 6 is not opened, so that the bypass path is closed. Therefore, in the hydraulic shock absorber, one oil chamber R1 is attenuated. It communicates with the other oil chamber R2 through the valve 21.

  When the movement stroke of the guide rod 92, that is, the other input portion 94 becomes equal to or greater than the dead zone stroke L2, the push member 94a in the other input portion 94 comes into contact with the tip of the input shaft 61 in the control valve 6, and the push member 94a is Since the spring force of the urging spring 94b that urges overcomes the spring force of the urging spring 64 in the control valve 6, the input shaft 61 moves backward as the push member 94a advances, and the other control valve 6 opens. To do.

  At this time, since the bypass path is opened, in the hydraulic shock absorber, one oil chamber R1 tends to communicate with the other oil chamber R2 through the opened bypass path. The high damping force that has been generated until then becomes lower.

  Then, when the operation is continued in the hydraulic shock absorber and the guide rod 92 continues to rise, it is the same as described above until the movement stroke of the other input portion 94 exceeds the operation stroke of the other control valve 6, When the operating stroke of the other control valve 6 is exceeded, the forward movement of the push member 94a is blocked.

  At this time, the backward movement of the control valve 6 may be mechanically prevented to prevent the push member 94a from moving forward, and the push member 94a may interfere with the housing portion 42, for example. It may be possible to prevent the forward movement.

  In addition, when the operation of the hydraulic shock absorber continues even after the control valve 6 is prevented from moving backward, there is no operation stroke in the control valve 6, and therefore the push member 94a contracts the biasing spring 94b. fall back.

  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 protrudes and retracts with respect to the cylinder body 1, the corresponding control valve 5 and 6 are opened to switch the bypass path to the communication state.

  Therefore, from this, in the valve device of the present invention, when the dead zone strokes L1, L2 are the same, it can be estimated that 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 state of the piston body 2 with respect to the cylinder body 1 can be manifested by making the dead zone strokes L1 and L2 the same.

  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, there is no problem even if it is assumed that the hydraulic shock absorber is in a neutral state by making the dead zone strokes L1 and L2 the same.

  In view of the above, in the present invention, when installing the hydraulic shock absorber, the neutral state in the valve device can be seen with certainty, and a conventional hydraulic shock absorber of the kind is installed. Therefore, the so-called neutral state is not easily displayed, and therefore, quick installation work can be realized as compared with the case where labor is required to install the hydraulic shock absorber.

  In the valve device of the present invention, the control valves 5 and 6 are opened by the operation of the input means 9, but the operation of the input means 9 is regarded as important by the control valve. It is assumed that the operation of 5 and 6 is requested, and the participation of the input means 9 is stopped after the request is lost.

  That is, in the control valves 5 and 6 shown in the figure, for example, when the poppet as the valve bodies 52 and 62 is set to fully open the bypass path by retreating by 30 m / m, the subsequent retreat of the poppet is nothing. Makes sense.

  Therefore, the input means 9 is involved until the poppet moves back the set amount, but thereafter the input means 9 is not involved, that is, the thrust from the input means 9 is not input to the control valves 5 and 6. is doing.

  Specifically, in the illustrated case, when the poppet is retracted by a certain amount in the control valves 5 and 6, further retreat is mechanically prevented in the control valves 5 and 6.

  That is, for example, since the backward movement of the control valve 5 is prevented, regardless of the movement of the control valve 5, the one input portion 93 moves backward against the spring force of the urging spring 93 b and the hydraulic shock absorber Follow the movement.

  In the same way, when the control valve 6 is prevented from retreating in the same situation, the input means 9 can be compared with the other input portion 94 against the spring force of the biasing spring 94b. Will follow the movement of the hydraulic shock absorber.

  Therefore, the input means 9 in the valve device of the present invention does not input excessive thrust to the control valves 5 and 6 that have been mechanically stopped. It becomes easy to guarantee the operability in the valve device permanently.

  Further, in the valve device of the present invention, it is sufficient that the opening operation stroke of the control valves 5 and 6, that is, the effective stroke is guaranteed, so that the control valves 5 and 6 are made compact, that is, the valve device is compact. May be possible.

  In the above description, it is assumed that so-called avoidance of the input means 9 is based on the stroke end in the control valves 5 and 6, but as long as the effective stroke in the control valves 5 and 6 is guaranteed, as described above, The input portions 93 and 94 may be brought into contact with the housing portion 42 which is the valve mount 4.

  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. In addition, a buffer that uses a fluid other than gas, which is a so-called non-shrinkable fluid, 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, it can be said that a neutral state in the hydraulic shock absorber can be realized.

  Further, in the valve device according to the present invention, in the embodiment of the control valves 5 and 6, this is not formed uniaxially, but formed biaxially. Alternatively, in consideration of the case where it is installed in the cylinder body 1, it is possible to avoid the inconvenience that it is easy to prevent the valve mount 4 from being reduced in size or to make the installation in the cylinder body 1 disadvantageous. This is advantageous.

  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 One control valve 6 The other control valve 9 Input means 21, 22 Damping valve 31 One rod body which comprises a rod body 32 The other rod body which comprises a rod body 42 Housing portion 51, 61 constituting the valve mount 51, 61 Input shaft 52, 62 Valve body 53, 63 Base shaft 54, 64 Energizing spring 91 Guide pipe 92 Guide rod 93 One input portion 93a, 94a Push member 93b, 94b Energizing means Energizing spring 94 Other input part 95 Arm member L1, L2 Dead band stroke R1, R2 Oil chamber

Claims (8)

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,
The sliding direction of the piston body said input means in said cylinder body of the base end to the piston body is a tip is continuously provided connected to the rod member to project into the cylinder outside the hydraulic damper in the hydraulic shock absorber a guide pipe for retractable penetrates the valve mount while along the guide rod is inserted into retractably into the guide pipe moves in synchronism with the sliding of the piston body, and to the other end of the guide rod and the other input unit is arranged between the neighboring to the other end of the guide pipe opposed to the other control valves in the bypass passage, the other end of the guide pipe to close one end and to the guide rod disposed between and the and a one input section opposite to said one control valve in the bypass passage, the input portion of the each side A push member which faces the serial control valve, is arranged behind the side of the push member and biasing means for biasing the push member in the forward direction,
The valve device according to claim 1, wherein an urging force of the urging means for urging the push member is superior to a spring force of the urging spring in the control valve . 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. An input shaft retreats thrust is input to tip from said input means said control valve faces, while being provided continuously to one end of the input shaft and the valve body for opening the bypass passage at the time of retraction, the The valve device according to claim 1 , further comprising a base shaft that defines a chamber communicating with the atmosphere while being connected to the valve body. The rod body and the claim 1 and the guide rod is coupled with the arm member tip proximal end is continuously provided on the piston body be in the hydraulic shock absorber projects into the cylinder outside, claim 2 or The valve device according to claim 3. The said input part in the said input means has a dead zone stroke between the said control valve and the said push member which opposes this control valve , The claim 3, Claim 3, or Claim 4 Valve device. Valve according to the control claim 1, the distal end of the input shaft in the valve is to allow the length adjustment of the axial length, according to claim 2, claim 3, claim 4 or claim 5 which is opposed to the input means apparatus. Claim 1 comprising a poppet or spool the valve body in the control valve to open and close the bypass passage, according to claim 2, claim 3, claim 4, the valve device according to claim 5 or claim 6 . The said bypass path is closed with 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 1, Claim 3, Claim 4 , 5. The valve device according to claim 6, 6 or 7.

Images