JP4921314B2 - 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, when the above-described hydraulic shock absorber is used as a vibration damper in a building, it is essential that the hydraulic shock absorber itself has a so-called margin in the expansion and contraction stroke. However, for this reason, in the valve device disposed in the bypass passage, it is necessary that the operation stroke of the spool as the control valve be the same as the operation stroke of the hydraulic shock absorber.

  As a result, in the valve device described above, the spool constituting the valve device is lengthened, so that the workability of the spool is deteriorated and it is difficult to maintain accuracy. Even in actuality, there is a risk that oil leakage is likely to occur, which becomes a problem when the hydraulic shock absorber is used as a vibration damping damper in a building.

The present invention has been developed in view of the above-described present situation, and the object of the invention is to exhibit a predetermined valve function, for example, as a damping damper in a building. To provide a valve device suitable for implementation in a hydraulic shock absorber.

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 And an input means for individually opening the two control valves to open them, and the control valve is connected to the valve mount, and the bypass passage is connected to the input shaft. a valve body for opening and closing a and a valve element biasing spring for biasing the valve body from the back side, the input means in the cylinder body in the hydraulic shock absorber During sliding of the serial piston body by opening operation of the control valve in the valve arrangement comprising by opening the bypass passage,
The tip the input means protrudes from the valve mount of the input shaft of the piston member in the proximal is continuously provided with the control valve while being held to the rod member to project the tip to the cylinder outside in the hydraulic shock absorber Having opposing drive members,
With the control valve closes the bypass passage during forward of the valve body which is biased from behind by the valve body biasing spring,
Are continuously formed on the valve body tip facing the driving member has an input restricting mechanism at the distal end of the input shaft to project from the valve mount,
A slide rod which this input restriction mechanism to face the retractable held by the tip while in the same moving direction and the axis direction of the input shaft to the distal end to the drive member in said input shaft, behind the side of the slide rod the slide rod is disposed and a biasing means for advancing toward the drive member,
The spring force of the biasing means is superior to the resultant force of the spring force of the valve body biasing spring and the frictional force when the control valve is operated,
Additional thrust the input regulating mechanism when entering from said input means to said control valve retracts the valve body in the contraction of the valve body biasing spring by the input and opening the bypass passage thrust from said input means and permitting retraction of the slide rod and formed by prevent further retraction of the input shaft in the control valve.

  Therefore, according to the present invention, the input means for inputting the thrust for operating the control valve disposed in the bypass passage for communicating both the oil chambers in the hydraulic shock absorber outside the cylinder body is provided in the piston body in the cylinder body. While operating the control valve during sliding to open the bypass path, it is possible to stop further operation for the control valve that has opened the bypass path by its operation, so the so-called expansion and contraction in the hydraulic shock absorber to which the input means is connected Even if the stroke exceeds the operating stroke in the control valve, that is, exceeds the effective stroke, the input means does not input a thrust force for further operating the control valve.

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

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

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

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

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

  On the other hand, according to the present invention, the input restricting mechanism for preventing the input of further thrust from the input means to the control valve having the bypass path opened is accommodated in the tip end portion of the input shaft in the control valve that projects the tip from the valve mount. Therefore, the configuration around the tip of the control valve can be simplified as compared with the case where the input restriction mechanism is arranged around the tip of the input shaft.

  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 the cylinder body 1 and both oil chambers having the same cross-sectional area in the cylinder body 1 while being slidably housed in the cylinder body 1, that is, A piston body 2 that defines an upper oil chamber R1 in the figure and a lower oil chamber R2 in the figure, and the oil chambers R1 and R2 while the base end is connected to the piston body 2 The rod body 3 is inserted through the shaft core portion of the cylinder body 1 and protrudes from the closed end of the cylinder body 1 to the outside. And the other rod body 32.

  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 drawing, the cylinder body 1 has a sub-cylinder body having the same diameter as the cylinder body 1 at the lower end side in the drawing. 11 is connected coaxially, the tip end side which is the lower end side in the figure of the other rod body 32 is made conductive in the sub-cylinder body 11, and the lower end side of the other rod body 32 interferes with a so-called other part. The sub cylinder body 11 has a bracket 12 that 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 be opened when the upstream pressure exceeds the cracking pressure, and the cracking pressure is arbitrarily set.

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

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

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

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

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

  At this time, 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 the so-called neutral region and reaches the vicinity of the stroke end where the piston body 2 approaches the end of the cylinder body 1, the opening opened in 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 is disposed in a passage that connects the high pressure side and the low pressure side, that is, a bypass that enables communication outside the cylinder body 1 of both the oil chambers R1 and R2. Control valves 5 and 6 that are arranged in the road and move by the input of thrust from the outside to open the bypass path, and a check for rectifying the flow of hydraulic oil in the bypass path with respect to the control valves 5 and 6 It has valves 7 and 8, input means 9 for inputting thrust to the control valves 5 and 6, and further has an input restriction mechanism 10.

  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, and the housing portion 42 is formed in both the oil chambers R1, R1. Control valves 5 and 6 permitting communication in opposite directions between R2 and check valves 7 and 8 for regulating the flow direction of hydraulic oil in the bypass passage, that is, rectifying.

  At this time, in view of the original function of the bypass path, it is the valve device according to the present invention that the valve mount 4 is held by the cylinder body 1 regardless of whether or not the valve mount 4 is formed. That is preferable.

  That is, as will be described later, in the valve device of the present invention, the control valves 5 and 6 arranged in the bypass passage are opened and closed via the input means 9 but depending on the expansion / contraction position of the hydraulic shock absorber. Since it is required to operate, at least 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 preferably integrally connected to the cylinder body 1 and held by the cylinder body 1.

  Next, the control valves 5 and 6 are operated so as to be opened by an input from the input means 9 following the protrusions and depressions of the rod body 3 with respect to the cylinder body 1 in the hydraulic shock absorber. Communicate with the oil chamber.

  That is, for example, in the control valve 5, when the hydraulic shock absorber in which one rod body 31 is immersed in the cylinder body 1 is switched to the open state by the input from the input means 9 and the other oil chamber R2 is switched. Is communicated with one of the oil chambers R1 through the opened control valve 5, and at this time, the control valve 6 is maintained in a shut-off state in its own state because the check valve 8 is operated. Close the bypass as far as possible.

  Even in the control valve 6, when one rod body 31 protrudes from the cylinder body 1, it is switched to the open state by the input from the input means 9 during the extension side operation, and one oil chamber R 1 is opened. The control valve 5 communicates with the other oil chamber R2 via the control valve 6. At this time, the control valve 5 maintains the shut-off state in its own state because the check valve 7 operates in the same manner as described above. To that extent, the bypass is closed.

  As for check valves 7 and 8, as described above, for example, when the control valve 5 is opened by the pressure side operation of the hydraulic shock absorber, it is checked that the hydraulic oil in the oil chamber R2 flows into the control valve 6. When 8 is blocked and the control valve 5 returns to the so-called return direction, that is, the hydraulic oil flowing out from the oil chamber R1 is not yet shut off because the hydraulic shock absorber is reversed to the extension side operation. The check valve 7 functions to prevent this and maintain the control valve 5 in a predetermined closed state when a situation flows into the engine, and only the damping valve 21 is operated in the hydraulic shock absorber so as to have a predetermined size. A damping force is generated.

  Then, the check valve 7 prevents the hydraulic oil in the oil chamber R1 from flowing into the control valve 5 when the control valve 6 is opened by the extension side operation of the hydraulic shock absorber, and the control valve 6 returns so-called. In other words, when the hydraulic shock absorber reverses to the pressure side operation, the check valve 8 prevents this when the hydraulic oil flowing out from the oil chamber R2 flows into the control valve 6 that is not yet shut off. Thus, while functioning to maintain the control valve 6 in a predetermined closed state, only the damping valve 22 operates in the hydraulic shock absorber to generate a damping force having a predetermined magnitude.

  From 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 by the control valves 5 and 6. With the cooperation of the valves 7 and 8, the displacement characteristic of the damping force as shown in FIG. 2 is obtained.

Here, regarding the control valves 5 and 6, the control valves 5 and 6 are, as shown in FIG. 1, input shafts 51 and 61 accommodated in the housing portion 42 of the valve mount 4 , and valve bodies 52 and 62. The base shafts 53 and 63 and the valve body biasing springs 54 and 64 are provided.

  The input shafts 51 and 61 are configured to input the thrust from the opposing input means 9 to the tip which is the upper and lower ends in the figure, and are composed of spools having the same axial direction as the rod body 3 described above.

  In the input shafts 51 and 61, there are one kerf 51a and 61a (see FIG. 1) as oil passages that realize flow rate control according to displacement in front of valve bodies 52 and 62, which will be described later. A plurality of lines are formed.

  In addition, the input shafts 51 and 61 are provided with dead zone strokes L1 and L2 which will be described later between the tip and the input means 9 while the tips facing the input means 9 project outside the housing portion 42 and are placed in the atmosphere. Yes.

  Further, as shown in FIG. 3, the input shafts 51 and 61 have a tip portion having an input restricting mechanism 10 as shown in FIG. 3. The input restricting mechanism 10 will be described later.

  Next, the valve bodies 52 and 62 are in series with the base ends of the input shafts 51 and 61, as shown in FIG. When the valve is moved backward, the bypass passage is opened. In the drawing, it is made of a poppet. Therefore, compared with the case where the valve bodies 52 and 62 are made of a spool, the hydraulic oil leaks effectively in the bypass passage. Stop.

  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.

  By the way, as described above, in the control valves 5 and 6, the input shafts 51 and 61 in front of the valve bodies 52 and 62 are cut into grooves 51a as oil passages that realize flow control according to the displacement. One or a plurality of 61a (see FIG. 1) is formed on the input shafts 51 and 61.

  Therefore, since the control valves 5 and 6 have the cut grooves 51a and 61a on the upstream side of the poppets 52 and 62, the flow of hydraulic oil through the cut grooves 51a and 61a is prevented. The flow rate can be controlled according to the stroke. For example, the waveform in the region indicated by the symbol X in the characteristic diagram of FIG. 2 can be controlled. Can alleviate the so-called shock without suddenly opening and closing.

  Next, the base shafts 53 and 63 are connected to the valve bodies 52 and 62 in series, that is, in the illustrated case, the shaft diameters of the base shafts 53 and 63 are integrated with the rear ends of the valve bodies 52 and 62 while the shaft diameters thereof are the same as the input shafts 51 and 61. The rear end is the same in the atmosphere.

  Therefore, in this valve device, the rear ends of the base shafts 53 and 63 are placed in the atmosphere, while the tips of the input shafts 51 and 61 having the same diameter are also placed in the atmosphere. It is maintained in the forward state only by the spring force of the valve body biasing springs 54 and 64, that is, it is maintained in a state in which the bypass passage is closed.

  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. Then, the flow of hydraulic oil in the bypass passage through the valve bodies 52 and 62 is allowed.

  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 a so-called valve seat portion and the bypass passage is maintained in a closed state, the valve body attached with a valve body 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.

  By the way, as described above, in the present invention, the tip end portions of the input shafts 51 and 61 have the input restricting mechanism 10, and the input restricting mechanism 10 includes a slide rod as shown in FIG. 13 and biasing means 14.

  The slide rod 13 is located at the distal end of the input shafts 51 and 61 and is held so as to be able to project and retract at the distal end while making the movement direction and the axial direction of the input shafts 51 and 61 the same. Make them face each other.

  At this time, the base end of the slide rod 13 is held in the input shafts 51 and 61 under an appropriate retaining structure, and does not come out of the input shafts 51 and 61 even when biased by the biasing means 14 described later. It is said.

  The urging means 14 is disposed at the front end of the input shafts 51 and 61 and is disposed behind the slide rod 13, and the urging force advances the slide rod 13 toward the input means 9 described later.

  The urging means 14 is composed of a coil spring housed in a chamber (not shown) formed at the tip of the input shafts 51 and 61 as shown in the figure. When this is formed in a sealed structure, it can be expected that the air spring force is exerted when the chamber is contracted by the retraction of the slide rod 13, and therefore the coil spring forming the urging means 14 can be made light.

  The spring force of the coil spring as the urging means 14 exceeds the resultant force of the spring force of the valve body urging springs 54 and 64 and the friction force when the control valves 5 and 6 are operated.

  Therefore, when the thrust from the input means 9 is input to the tip of the slide rod 13, the biasing means 14 prevents the slide rod 13 from retreating at the tip of the input shafts 51 and 61.

  Therefore, in the control valves 5 and 6, when the thrust from the input means 9 is input, first, the valve body biasing springs 54 and 64 contract and the input shafts 51 and 61 are immersed in the valve mount 4. The control valves 5 and 6 are opened to allow reverse movement.

  When the control valves 5 and 6 are opened and no further opening operation is required, the input shafts 51 and 61 do not move back further in the control valves 5 and 6. When the thrust is input, the biasing spring as the biasing means 14 contracts and the slide rod 13 is retracted, and the thrust from the input means 9 is not input to the control valves 5 and 6.

  Incidentally, when the input means 9 retreats from the above state, first, the urging spring as the urging means 14 is extended, and the slide rod 13 protrudes from the tip portions of the input shafts 51 and 61.

  After the slide rod 13 is prevented from projecting, the input shafts 51 and 61 of the control valves 5 and 6 project from the valve mount 4 and return to the old state due to the extension of the valve body biasing springs 54 and 64.

  In view of the above, when the thrust from the input means 9 is input to the input shafts 51 and 61 of the control valves 5 and 6, the urging means 14 has the input shaft 51 according to the moving stroke amount of the input means 9. , 61 is sufficient.

  As described above, the control valves 5 and 6 open the bypass passage by the input of thrust from the outside by the input means 9, but this input means 9 basically synchronizes with the movement of the hydraulic shock absorber. The control valves 5 and 6 are opened, and a pair corresponding to the control valves 5 and 6 is provided as shown in FIG.

  The input means 9 includes, as shown in the figure, one drive member 91 composed of an arm member connected to one rod body 31 that is upper in the figure and the other rod body 32 that is lower in the figure. The other drive member 92 which consists of an arm member similarly connected with this.

  At this time, since the input means 9 is configured to have only the drive members 91 and 92 made of so-called arm members, the input means 9 can be made compact.

  In the input means 9, one drive member 91 is arranged outside the cylinder body 1, but the other drive member 92 is a slit-shaped opening 11 a formed in the sub-cylinder 11. The tip side protrudes outside the cylinder body 1 so to speak.

  Therefore, the width of the slit-shaped opening 11a formed in the sub-cylinder body 11 is set to a dimension that substantially matches the width of the other driving member 92, so that the opening 11a and the other driving member 92 are connected to the rod body. 3 functions as a detent for the cylinder body 1.

  Incidentally, as described above, the dead zones L1 and L2 appear between the distal ends of the drive members 91 and 92 and the distal ends of the control valves 5 and 6, respectively.

  Therefore, in this input means 9, for example, when one rod body 31 is immersed in the cylinder body 1, until the rod body 31 is immersed in the cylinder body 1 more than the dead zone stroke L1 described above. The drive member 91 does not interfere with the tip of the input shaft 51 in the control valve 5, so that the control valve 5 does not open.

  When the stroke in which the rod body 31 is immersed in the cylinder body 1 is equal to or greater than the dead zone stroke L1, the drive member 91 comes into contact with the tip of the input shaft 51 in the control valve 5, and the input shaft 51 is connected to the valve mount 4 The control valve 5 is thus opened and immersed.

  In addition, the above-described operation is similar to the operation of the drive member 92 on the opposite side of the input means 9 with respect to the input shaft 61 of the control valve 6 when the other rod body 32 is immersed in the cylinder body 1. Therefore, the control valve 6 operates in the same manner as the control valve 5 described above.

  Further, when the control valves 5 and 6 are in a state where the poppets 52 and 62 are mechanically prevented from retreating, the retraction of the input shafts 51 and 61 is stopped. The urging spring as the urging means 14 is contracted, and the slide rod 13 is immersed in each of the input shafts 51 and 61.

  As a result, in the valve device of the present invention, when the rod body 3 is immersed in the cylinder body 1 in the hydraulic shock absorber, the control valves 5 and 6 are opened to open the bypass path, but the bypass path is opened. Thereafter, the control valves 5 and 6 are not further opened.

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

  Therefore, from this, it can be said that in the valve device of the present invention, when the dead zone strokes L1, L2 are the same, the hydraulic shock absorber is in a so-called neutral state.

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

  At this time, even if the piston body 2 is not in a completely neutral state in the cylinder body 1, in many cases, the deviation will be larger than the so-called tolerance, but it will not be unnecessarily large. By adjusting the strokes L1 and L2 to be the same, it can be said that there is no problem even if it is assumed that the hydraulic shock absorber is 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. Therefore, it is possible to realize a quick installation work as compared with the case where the installation of the hydraulic shock absorber is troublesome.

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

  In the above description, the present invention is embodied in a double rod type hydraulic shock absorber. However, from the point of view of the present invention, the present invention is embodied in a single rod type hydraulic shock absorber. 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.

  Further, in the above description, the input means 9 is directly attached to the rod body 3, but instead of this, although not shown, it is provided on a guide rod connected to the rod body 3 and provided in parallel with the rod body 3. In addition, although the input restriction mechanism 10 is provided at the tip of the input shafts 51 and 61, this input restriction mechanism 10 may be provided on the input means 9 side, although not shown in the figure.

It is a principle figure showing one embodiment of a hydraulic shock absorber provided with a valve device by 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 the elements on larger scale which show the front-end | tip part of the input shaft in a control valve with an input means and a biasing means.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Cylinder body 2 Piston body 3 Rod body 4 Valve mount 5,6 Control valve 9 Input means 10 Input control mechanism 13 Slide rod 14 Energizing means 21,22 Damping valve 51,61 Input shaft 52,62 Valve body 53,63 Base shaft 54, 64 Valve body biasing spring 91, 92 Drive 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 An input shaft in which the control valve is accommodated in the valve mount; a valve body that is connected to the input shaft to open and close the bypass path; and a valve body biasing spring that biases the valve body from the rear side. It has, during sliding by opening operation of the control valve is opening the bypass passage of the piston member in the cylinder body said input means in the hydraulic shock absorber In the valve apparatus comprising Te,
The tip the input means protrudes from the valve mount of the input shaft of the piston member in the proximal is continuously provided with the control valve while being held to the rod member to project the tip to the cylinder outside in the hydraulic shock absorber Having opposing drive members,
With the control valve closes the bypass passage during forward of the valve body which is biased from behind by the valve body biasing spring,
Are continuously formed on the valve body tip facing the driving member has an input restricting mechanism at the distal end of the input shaft to project from the valve mount,
A slide rod which this input restriction mechanism to face the retractable held by the tip while in the same moving direction and the axis direction of the input shaft to the distal end to the drive member in said input shaft, behind the side of the slide rod the slide rod is disposed and a biasing means for advancing toward the drive member,
The spring force of the biasing means is superior to the resultant force of the spring force of the valve body biasing spring and the frictional force when the control valve is operated,
Additional thrust the input regulating mechanism when entering from said input means to said control valve retracts the valve body in the contraction of the valve body biasing spring by the input and opening the bypass passage thrust from said input means valve apparatus characterized by comprising to permit retraction of the slide rod to prevent further retraction of the input shaft in the control valve. Identical with, the cross-sectional area by connecting the proximal end to the piston body having a damping valve in which the hydraulic shock absorber to allow the communication between the both oil chambers in the piston body slidably accommodated within the body the cylinder valve device according to claim 1 tip by inserting the shaft core portion of the both oil chamber comprising a rod of both the one and the other to protrude above the cylinder outside while the. And the input shaft to retract the 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 a base shaft defining a volume chamber communicating with the atmosphere while being continuously provided to the valve body, the valve element biasing spring for biasing in the forward direction the valve body via the cornerstone while being accommodated in the vessel chamber The valve device according to claim 1 or 2, comprising: The valve device according to claim 1, 2 or 3, wherein the valve body in the control valve has a poppet or a spool for opening and closing the bypass passage. Claim 1, wherein the biasing means in the input regulating mechanism comprises a coil spring, according to claim 2, the valve device according to claim 3 or claim 4. The thrust from the said input means is made into the axial force accompanying the protrusion and protrusion of the said rod body with respect to the said cylinder body in the said hydraulic buffer, The claim 3, Claim 3, Claim 4 or Claim 5 Valve device. The valve device according to claim 1, 2, 3, 4, 5, or 6, wherein a tip end portion of the slide rod can be adjusted in length. 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 .

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