JP4895970B2 - 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.

  In order to achieve the above-described object, the configuration of the valve device according to the present invention basically includes a bypass passage that allows both oil chambers defined by the piston body to communicate with each other outside the cylinder body in the cylinder body of the hydraulic shock absorber. One control valve disposed on each valve mount forming the bypass path and enabling opening and closing in one direction in the bypass path, and the other control valve enabling opening and closing in the other direction in the bypass path. Input means for individually opening the control valve to open the control valve, and the input means opens the control valve to open the bypass when the piston body slides in the cylinder body of the hydraulic shock absorber. In addition, in the valve device which enables further stop of the opening operation for the control valve which opened the bypass path, the input means is hydraulic A guide rod that penetrates the valve mount while being along the sliding direction of the piston body in the impactor and makes one end abut the fixed side, and the other input that is held by the other end of the guide rod and faces the other control valve And an input portion that is movably interposed in the middle portion of the guide rod and faces one of the control valves in the bypass path, and has a detent mechanism between the valve mount and the guide rod, It is assumed that a detent mechanism is provided between the guide rod and the one input part.

  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.

  On the other hand, it has a detent mechanism between the valve mount and the guide rod, and a detent mechanism between the guide rod and one input part, so that the input operation of thrust to the control valve by each input part is guaranteed. Is done.

  The rotation prevention mechanism has a valve mount and a guide pin whose base end is held by the one input portion, and a groove on the outer periphery of the guide rod that extends in the axial direction of the guide rod so that the tip end portion of the guide pin is exposed. Therefore, it is possible to hardly expose the structure of the rotation prevention mechanism to the outside. For example, it is not necessary to worry about malfunction of the rotation prevention mechanism due to dust adhesion.

  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. Thus, this 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 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 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 has a 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 at the lower end side in the drawing. It is connected to the same axis, 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 to prevent the lower end side of the other rod body 32 from interfering with a so-called other part. The sub-cylinder body 11 has a bracket 12 that enables the so-called attachment of the hydraulic shock absorber.

  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 bracket 33 can be used to connect to the stationary side B of the hydraulic shock absorber.

  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. have.

  At this time, the so-called both ends of the bypass path communicate 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, the opening opened in the cylinder body 1 also reaches the vicinity of the stroke end approaching the end of the cylinder body 1. Is not blocked and the communication of the oil chambers R1, R2 to the bypass 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 plate portion 41 and the housing portion 42 in the valve mount 4 integrally connected to the cylinder body 1, and the housing portion 42 is paired between the oil chambers R1 and R2. Control valves 5 and 6 are arranged in parallel so as to allow communication in opposite directions, and check valves 7 and 8 that control the flow direction of hydraulic oil in the bypass passage, that is, rectify. .

  At this time, in view of the original function of the bypass path, it is the valve device of the present invention that the valve mount 4 is held by the cylinder body 1 aside from being formed in the valve mount 4. In other words, 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 required to open and close depending on the expansion / contraction position of the hydraulic shock absorber. In the valve mount 4 having the control valves 5 and 6, this may be simulated by a part of the cylinder body 1. Therefore, from this viewpoint, the valve mount 4 is integrally connected to the cylinder body 1. It is preferably provided 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, the hydraulic shock absorber in which one rod body 31 is immersed in the cylinder body 1 is switched to an open state by the input from the input means 9 when contracting, 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 through the opened other control valve 6, and at this time, one control valve 5 is operated by the check valve 8 as described above, In this state, the shut-off state is maintained, and as long as it is closed, 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 contraction of a hydraulic buffer in which one rod body 31 is immersed in the cylinder body 1, the cylinder body is opened. When the check valve 7 prevents the hydraulic oil in the oil chamber R2 in 1 from flowing into the other control valve 6 and one control valve 5 comes back, that is, from the cylinder body 1 to one rod The check valve 8 is turned on when the hydraulic oil flowing out from the oil chamber R1 in the cylinder body 1 flows into the one control valve 5 that is not yet shut off by reversing the extension in which the body 31 protrudes. This function is prevented so that one control valve 5 is maintained in a predetermined closed state, and the damping valve 21 of the piston body 2 in the hydraulic shock absorber is provided. It is operated and generates a damping force of a predetermined magnitude.

  When the other control valve 6 is opened by the extension of the hydraulic shock absorber in which one rod body 31 protrudes from the cylinder body 1, the hydraulic oil in the oil chamber R1 in the cylinder body 1 is moved to the one control valve 5. When the check valve 8 prevents the other 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 inside of the cylinder body 1 is reversed. When the hydraulic fluid flowing out from the oil chamber R2 flows into the other control valve 6 that has not yet been shut off, the check valve 7 prevents this and closes the other control valve 6 to a predetermined closed state. In addition to functioning to maintain the state, only the damping valve 22 of the piston body 2 in the hydraulic shock absorber is operated to generate a damping force of a predetermined magnitude.

  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 with the control valves 5 and 6. With the cooperation of the check valves 7 and 8, a damping force displacement characteristic 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 valve body biasing springs 54 and 64.

  That is, first, the input shafts 51 and 61 input the thrust from the input means 9 which opposes to the front-end | tip, and the axial direction is made the same with the rod body 3 mentioned above in the figure.

  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 the hydraulic oil from leaking in the bypass passage as compared with the case where the valve bodies 52 and 62 are made of only 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 region indicated by the symbol X in the characteristic diagram of FIG. 2 can be controlled, and the valve bodies 52 and 62 can be suddenly opened and closed even when control of this waveform is not required. There is no so-called shock can be alleviated.

  In addition, about said valve body 52,62, this may consist of spools, and when it consists of spools, you may have 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. 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. It is maintained in the forward state only by the spring force of the valve body urging springs 54 and 64, which will be described later, that is, the state in which the bypass passage is closed is maintained.

  Although the valve body biasing springs 54 and 64 are coil springs as shown in the drawing, the so-called identity is not required as long as the biasing force in each of the valve body biasing springs 54 and 64 is not extremely small. .

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

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

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

  On the other hand, the input means 9 is basically formed so as to follow the movement of the rod body 3 described above, and in the drawing, the sliding direction of the piston body 2 in the hydraulic shock absorber, that is, the rod body 3 It has a guide rod 91 that can be moved in the vertical direction in the drawing through the housing portion 42 in the valve mount 4 along the moving direction, and one end that is the upper end in the drawing in the drawing is the fixed side. It is made to contact B.

  Incidentally, instead of bringing one end of the guide rod 91 into contact with the fixed side B as shown in the drawing, it may be brought into contact with a receiving base as a bracket protruding from the rod body 3, although not shown.

  The illustrated guide rod 91 has stroke adjusting means (not shown) formed in an adjuster structure at an end that faces the fixed side B. The stroke adjusting means is an end of the guide rod 91. The cap nut 91a is screwed to the portion, and the stroke with respect to the fixed side B is adjusted by advancing and retreating at the end of the guide rod 91 of the cap nut 91a.

  In the input means 9, the guide rod 91 is held at the other end which is the lower end in the drawing and faces the other control valve 6, and inputs a thrust at the time of forward advancement in the drawing. The other input portion 91c is integrally provided, is movably provided in the intermediate portion, and faces one control valve 5 in the bypass passage, and inputs the thrust at the time of forward movement that is lowered in the drawing. 91b.

  At this time, the one input portion 91b and the other input portion 91c are opposed to the tips of the input shafts 51 and 61 in the control valves 5 and 6 with a space therebetween, and this space is set to the dead zone strokes L1 and L2. .

  In the input means 9, the guide rod 91 has a secondary biasing spring 92 interposed between the one input portion 91 b and the fixed side B so as to be extendable and contractible.

  On the other hand, the guide rod 91 is integrally connected with a spring receiver 91d carrying one input portion 91b, and the main biasing member disposed between the spring receiver 91d and the housing portion 42 as the valve mount 4. A spring 93 is interposed.

  At this time, the spring force of the main urging spring 93 exceeds the spring force of the valve body urging spring 64 that urges the valve body 62 from the back side in the corresponding control valve 6, and the spring of the sub urging spring 92. The force exceeds the spring force of the valve body biasing spring 54 that biases the valve body 52 from the rear side in the corresponding control valve 5.

  The auxiliary biasing spring 92 is locked to a spring receiver 94 that is interposed in the vicinity of one end of the one input portion 91b and the guide rod 91 so as to be movable to the guide rod 91 under the locking of the snap ring 94a. .

  At this time, the one input portion 91b is vertically disposed in the figure on the cylindrically formed collar member 95 that is movably interposed on the guide rod 91 and is supported so as to be seated on the spring receiver 91d. It is held to allow sliding.

  The one input portion 91b is interposed on the outer periphery of the collar member 95. However, in relation to the rotation preventing mechanism 10 (see FIG. 4) described later, the one input portion 91b is arranged vertically on the outer periphery of the collar member 95. However, it may be interposed so that the rotation is prevented.

  Therefore, in the input means 9, one end, which is the upper end of the auxiliary biasing spring 92 in the drawing, faces the fixed side B, that is, in the same manner as the main biasing spring 93 in the drawing, as in the case of being locked. The one end which is the upper end faces the fixed side B through the spring receiver 91d.

  And in this input means 9, the guide rod 91 is in a posture to be pushed upward in the figure by the spring force of the main biasing spring 93, and therefore is in a posture to be always pressed against the fixed side B, and The extension stroke of the main biasing spring 93, that is, the stroke for lifting the guide rod 91 upward becomes longer than the stroke of the other control valve 6.

  As described above, in the valve device of the present invention, when the expansion / contraction amount exceeds the above-described 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, it is said that the corresponding control is performed. The 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 can be 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, i.e., neutral, it is possible to adjust the length of the tip of the guide rod 91 by using the stroke adjusting means formed in the adjuster structure, i.e., An adjustment operation is performed so that the dead zone strokes L1 and L2 are the same, and a so-called neutral state of the piston body 2 with respect to the cylinder body 1 can appear.

  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 is larger than the so-called tolerance, but does not become unnecessarily large. Therefore, the dead zone strokes L1, L2 By adjusting so that they are the same, there is no problem even if the hydraulic shock absorber is assumed to be in a neutral state.

  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, so that a quick installation operation can be realized as compared with the case where the installation of the hydraulic shock absorber is troublesome.

  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. In the scene where the operations 5 and 6 are requested, the participation of the input means 9 is stopped after the request disappears.

  That is, in the control valves 5 and 6 shown in the figure, for example, when the poppets 52 and 62 are set to fully open the bypass passage by retreating 30 m / m, the subsequent poppets 52 and 62 are not retreated. Makes sense.

  Therefore, the input means 9 is involved until the poppets 52, 62 move backward from 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, 6. It is said.

  Specifically, in the illustrated case, when the poppets 52 and 62 are retracted by a certain amount in the control valves 5 and 6, further retraction is mechanically prevented in the control valves 5 and 6.

  That is, for example, since the control valve 5 is prevented from moving backward, the input portion 91b moves backward against the spring force of the auxiliary biasing spring 92 regardless of the movement of the control valve 5, and the hydraulic shock absorber moves. Follow.

  In the case of the input means 9, when the control valve 6 is prevented from retreating in the same situation, the other input portion 91 c resists the spring force of the main urging spring 93. Then move backward to 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. The operability of the valve device is permanently guaranteed.

  Further, in the valve device of the present invention, 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 can be made compact, that is, the valve device can be made compact. Can be possible.

  In the above description, it is assumed that the so-called participation 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, instead of this, The input portion 91b and the other input portion 91c may be based on contact with the housing portion 42 that is the valve mount 4.

  Here, in the valve device according to the present invention, the operation of the input means 9 and the operation of the control valves 5 and 6 will be described with reference to FIG.

  First, (A) in FIG. 3 shows a dead zone stroke L1 that appears between one control valve 5 and one input portion 91b, and a dead zone stroke that appears between the other control valve 6 and the other input portion 91c. L2 is the same, and although not shown, also in the hydraulic shock absorber, the piston body 2 in the cylinder body 1 is in a neutral position and the input means 9 is in a so-called neutral state.

  Therefore, for example, the guide rod 91 moves rightward in the drawing and is in a state of being immersed in the housing portion 42 in the valve mount 4, so that the one input portion 91 b approaches the tip of the input shaft 51 in the one control valve 5. In some cases, the one input portion 91b does not interfere with the tip of the input shaft 51 in the control valve 5 until the guide rod 91 is immersed in the housing portion 42 beyond the dead zone stroke L1, and therefore, the one input portion 91b is not input to the input shaft 51. Until one of the control valves 5 is brought into contact with the front end of this, it does not open.

  When the stroke in which the guide rod 91 is inserted into the housing portion 42 of the valve mount 4 is equal to or greater than the dead zone stroke L1, the main biasing spring 93 is forcibly contracted as shown in FIG. Then, the one input portion 91b abuts on the tip of the input shaft 51 in the one control valve 5, and at this time, the spring force of the auxiliary biasing spring 93 that urges the one input portion 91b urges the input shaft 51. Since the spring force is surpassed, the input shaft 51 is immersed in the housing portion 42 of the valve mount 4, so that the one control valve 5 is opened.

  Further, when the operation is continued in the hydraulic shock absorber after the so-called valve stroke end where the opening operation of one control valve 5 is stopped, as shown in FIG. The right line is continued, and at this time, the one input portion 91b is put in a state where the movement is prevented by the one control valve 5, so that the auxiliary bias spring 92 contracts and the main bias spring 93 further contracts. The right line of the guide rod 91 is continued.

  On the other hand, when the guide rod 91 moves leftward in FIG. 3 and comes out of the housing portion 42 in the valve mount 4, the other input portion 91 c approaches the tip of the input shaft 61 in the other control valve 6. The other input portion 91c does not interfere with the tip end of the input shaft 61 in the control valve 6 until the guide rod 91 is immersed in the housing portion 42 more than the dead zone stroke L2, and therefore the other input portion 91c is the tip end of the input shaft 61. The other control valve 6 is not opened until it is brought into contact with.

  When the stroke in which the guide rod 91 is inserted into the housing portion 42 of the valve mount 4 is equal to or greater than the dead zone stroke L2, the other input portion 91c is connected to the other control valve 6 as shown in FIG. Since the spring force of the main urging spring 93 that abuts the tip of the input shaft 61 and urges the other input portion 91c is superior to the spring force that urges the input shaft 61, the input shaft 61 is valve-mounted. 4 is immersed in the housing part 42, so that the other control valve 6 is opened.

  In addition, when the operation is continued in the hydraulic shock absorber after the so-called valve stroke end where the opening operation of the other control valve 6 is stopped, the left line of the guide rod 91 is continued. The guide rod is placed so that the movement of the portion 91c is blocked by the other control valve 6, and the fixed side B follows the movement of the hydraulic shock absorber as shown in FIG. Go away from one end of 91.

  As described above, according to the present invention, the predetermined operation of the control valves 5 and 6 is realized when the input means 9 functions, but the rotation prevention mechanism 10 shown in FIG. This anti-rotation mechanism 10 prevents rotation about the guide rod 91 of the one input portion 91b and the other input portion 91c as a rotation axis.

  That is, as shown in the figure, the rotation prevention mechanism 10 is disposed between the housing portion 42 and the guide rod 91 in the valve mount 4 and is also disposed between the guide rod 91 and the one input portion 91b. Has been.

  First, the so-called detent mechanism 10 on the lower side in FIG. 4 includes a guide pin 101 disposed between the housing portion 42 and the other input portion 91c, and a groove 102 in which the guide pin 101 resides. Become.

  The guide pin 101 is a so-called pin, and a base end portion which is a left end portion in the drawing is held in a fixed state by a housing portion 42, for example, using a bolt (not shown). It is assumed that the front end portion serving as the right end portion is present in the groove 102.

  On the other hand, the groove 102 is provided on the outer periphery of the guide rod 91 and extends in the axial direction of the guide rod 91. The length of the groove 102 is determined by the dead zone stroke L2 for the control valve 6 and the control valve 6 after the operation. And a length including the stroke for opening the control valve 5 after the dead zone stroke L1 for the control valve 5 and the stroke for opening the control valve 5 are set.

  Thus, since the axial direction of the groove 102 is the same as the axial direction of the guide rod 91, the operation of the guide rod 91 in the housing portion 42 that is so-called intrusion is not hindered.

  Incidentally, in the illustrated case, when the guide pin 101 is connected to the groove 102, the other input portion 91c is set to face the other control valve 6. However, from the point of view of the present invention, the other input portion 91c is illustrated. However, after the rotation of the guide rod 91 relative to the housing portion 42 is prevented, the connection position of the other input portion 91c relative to the guide rod 91 may be selected.

  Next, the other anti-rotation mechanism 10 in the upper side in FIG. 4 includes a guide pin 103 disposed between the guide rod 91 and the one input portion 91b, and a groove 104 in which the guide pin 103 is present. Consists of.

  The guide pin 103 is a so-called pin like the guide pin 101 described above, and a base end portion which is a left end portion in the drawing is held by a collar member 95 which is one input portion 91b.

  That is, as shown in the figure, the one input portion 91b is held on the outer periphery of the interposed collar member 95 so as to be movable by the guide rod 91 as described above.

  Therefore, as shown in the figure, the guide pin 103 is held in a fixed state by screwing or press-fitting into the collar member 95, and in this state, the tip end portion which becomes the right end portion in the drawing. Is present in the groove 104.

  On the other hand, the groove 104 is formed on the outer periphery of the guide rod 91 and extends in the axial direction of the guide rod 91 in the same manner as the lower groove 102 described above, and its length is a dead zone for the control valve 5 described above. The length is set to include the stroke L1 and the stroke for opening the control valve 5 after the dredging.

  Even in the groove 104, the axial direction is the same as the axial direction of the guide rod 91, so that the movement of the one input portion 91 b in the so-called vertical direction relative to the guide rod 91 is not hindered.

  Incidentally, in the illustrated case, when the guide pin 103 is connected to the groove 104, the one input portion 91b is set to face the one control valve 5. However, from the point of view of the present invention, the input portion 91b is illustrated. However, after the rotation of the collar member 95 with respect to the guide rod 91 is prevented, the connection position of the one input portion 91b with respect to the collar member 95 may be selected.

  Therefore, in the anti-rotation mechanism 10 formed as described above, the guide rod 91 is prevented from rotating with respect to the housing portion 42 in the valve mount 4, and the one input portion 91b is rotated with respect to the guide rod 91. Therefore, in the input means 9, the input operation of thrust to the control valves 5 and 6 by the input portions 91b and 91c is guaranteed.

  And since this rotation prevention mechanism 10 is comprised by the guide pins 101 and 103 and the groove | channels 102 and 104 which make this guide pins 101 and 103 exist, the structure becomes simple and the complexity of the mischievous structure in a valve apparatus is complicated. Do not raise product costs unnecessarily.

  In addition, in the anti-rotation mechanism 10, it is possible to prevent the structure from being exposed to the outside. For example, it is not necessary to worry about malfunction of the anti-rotation mechanism 10 due to adhesion of dust.

  In addition, when the detent mechanism 10 is employed, when the hydraulic shock absorber equipped with the valve device of the present invention is installed at a predetermined position, the input portions 91b and 91c in the input means 9 are securely connected. The control valves 5 and 6 can be opposed to each other, so that so-called installability is improved.

  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.

  Furthermore, in the above description, in the hydraulic shock absorber equipped with the valve device according to the present invention, the case where the valve mount 4 is integrally held by the cylinder body 1 is taken as an example. 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 so that 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.

  Further, 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 on one axis but on two axes. Or, considering the case where it is installed in the cylinder body 1, there is an advantage that the miniaturization of the valve mount 4 is not hindered and that the installation in the cylinder body 1 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. It is a figure which shows the operation | movement aspect of an input means. It is the schematic which shows one Embodiment of a rotation prevention mechanism.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Cylinder body 2 Piston body 4 Valve mount 5 One control valve 6 The other control valve 9 Input means 10 Anti-rotation mechanism 21,22 Damping valve 51,61 Input shaft 52,62 Valve body 53,63 Base shaft 54,64 Valve body Energizing spring 91 Guide rod 91b One input portion 91c The other input portion 91d Spring bearing 92 Sub energizing spring 93 Main energizing spring 101, 103 Guide pin 102, 104 Groove R1, R2 Oil chamber

Claims (8)

In the hydraulic shock absorber, both the oil chamber defined by the piston body inside the cylinder body is connected to the outside of the cylinder body, and the valve mount that forms this bypass path is respectively arranged to open and close in one direction in the bypass path One control valve that enables and the other control valve that enables opening and closing in the other direction in the bypass path, and input means that individually inputs thrust to the two control valves and operates to open, the input means In the valve device, the control valve is opened when the piston body slides in the cylinder body in the hydraulic shock absorber to open the bypass path, and the control valve that opens the bypass path can be further stopped. One end of the input means penetrates the valve mount while following the sliding direction of the piston body in the hydraulic shock absorber. A guide rod to be brought into contact with the fixed side, the other input portion that is held at the other end of the guide rod and faces the other control valve, and is movably interposed in the middle portion of the guide rod, It has a one input part that faces the control valve, a non-rotating mechanism between the valve mount and the guide rod, and a non-rotating mechanism between the guide rod and the one input part. And valve device. The rotation prevention mechanism includes a valve mount and a guide pin whose proximal end is held by the one input portion, and a groove on the outer periphery of the guide rod that extends in the axial direction of the guide rod so that the distal end portion of the guide pin is present. The valve device according to claim 1. A spring bearing and a valve mount that have a secondary biasing spring disposed between the fixed side and the one input part while being interposed on the outer periphery of the guide rod, and that are connected to the guide rod and carry the one input part. The main urging spring is interposed between the outer periphery of the guide rod and is arranged between the main urging spring and the auxiliary urging spring. The valve device according to claim 1 or 2, wherein the valve body is superior to a spring force of a valve body energizing spring that energizes the valve body from behind. The hydraulic shock absorber has a damping valve that allows the oil body to communicate with the piston body slidable within the cylinder body, and the base end is connected to the piston body so that the cross-sectional area is the same while both oil The valve device according to claim 1, 2 or 3, further comprising both one and the other rod body that are inserted through the shaft core portion of the chamber and projecting the tip out of the cylinder body. An input shaft that moves backward by inputting the thrust from the input means facing the control valve, a valve body that is connected to one end of the input shaft and that opens the bypass when retracted, and is connected to the valve body. And a valve body biasing spring configured to urge the valve body in the forward direction through the base shaft while being housed in the chamber. The valve device according to claim 1, claim 2, claim 3 or claim 4. The valve device according to claim 1, 2, 3, 4, or 5, wherein a tip end portion of an input shaft in a control valve facing the input means can be adjusted in length. The valve device according to claim 1, 2, 3, 4, 5, or 6, wherein the control valve has a poppet or a spool as a valve body for opening and closing the bypass passage. The bypass path is closed by a control valve when the piston body is located near the center of the cylinder in the hydraulic shock absorber. Claims 1, 2, 3, 4, 5, 6 Or the valve apparatus of Claim 7.

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