JP2019158001A - Valve device and shock absorber - Google Patents

Abstract

To provide a valve device capable of preventing coming into a fail state during normal time even in the case where both pressure control and opening/closing of a passage are performed by a solenoid valve, capable of freely setting the characteristic of a passive valve in detail and capable of suppressing adsorption of a passive valve body, and to provide a shock absorber.SOLUTION: A valve device V includes: a pressure introduction passage P2; a first passage P3 and a second passage P4 connected to the downstream of the pressure introduction passage P2; a solenoid valve 4 for controlling the pressure on the upstream side by opening the first passage P3 and closing the second passage P4 during conduction time, and closing the first passage P3 and opening the second passage P4 during non-conduction time; and a passive valve 5 provided further on the downstream side than the solenoid valve 4 of the second passage P4. The passive valve 5 includes: a spherical passive valve body 50 moving onto and away from an annular passive valve seat 9f and for opening/closing the second passage P4; and a plate spring 51 for energizing the passive valve body 50 in a closing direction.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a valve device and a shock absorber provided with the valve device.

  The valve device is used, for example, as a damping valve that varies the damping force of a shock absorber interposed between a vehicle body and an axle.

  In such a damping valve, a main valve body that provides resistance to the flow of liquid generated when the shock absorber expands and contracts, and a pressure introduction that guides the pressure upstream from the main valve body to the back of the main valve body A passage, a first passage connected downstream of the pressure introduction passage, a pressure control valve body that controls a valve opening pressure when the first passage is opened, and an on-off valve body that opens and closes downstream thereof Including a solenoid valve, a pressure control valve body in the first passage and a second passage connected between the valve body and a passive valve provided in the second passage, and opens and closes when the solenoid valve is energized. There is one that opens the valve body to control the valve opening pressure of the pressure control valve body, and closes the on-off valve body when the solenoid valve is not energized to flow liquid to the passive valve (for example, Patent Document 1).

  According to the above configuration, when the power is normally supplied to the electromagnetic valve, the valve opening pressure of the pressure control valve body can be controlled to control the back pressure of the main valve body to the valve opening pressure of the pressure control valve body. If the back pressure of the main valve element is adjusted, the resistance of the main valve element changes. Therefore, if the back pressure is controlled, the damping force generated by the shock absorber can be increased or decreased to change the damping force characteristic. On the other hand, the liquid passes through the passive valve at the time of failure to cut off the power supply to the electromagnetic valve. For this reason, at the time of failure, the back pressure of the main valve body is determined by the setting of the passive valve. That is, even if the power supply to the electromagnetic valve is cut off, the shock absorber can exhibit a predetermined damping force, so that it becomes fail-safe.

JP 2014-173716 A

  The valve body (solenoid valve body) of the solenoid valve used in the above-described conventional damping valve has a configuration in which the pressure control valve body and the on-off valve body that opens and closes the downstream side thereof are integrated. At the same time, it moves linearly in the same direction. When the electromagnetic valve body moves to one side, the pressure control valve body approaches the corresponding valve seat (pressure control valve valve seat) and the on-off valve body leaves the corresponding valve seat (open / close valve valve seat). On the other hand, when the solenoid valve body moves to the other side, the pressure control valve body moves away from the pressure control valve valve seat and the on-off valve body approaches the on-off valve valve seat.

  The solenoid valve is a spring that pushes the solenoid valve body away from the pressure control valve body and the pressure control valve seat so that the on / off valve body is seated on the on / off valve seat, and the opposite direction to this spring And a solenoid that gives the thrust to the solenoid valve body. When the solenoid valve is energized, the solenoid valve body is pushed down against the biasing force of the spring by the thrust of the solenoid to open the on-off valve body, and the valve opening pressure of the pressure control valve body depends on the energization amount. The size is adjusted. On the other hand, when the solenoid valve is not energized, the solenoid valve body is pushed up to the maximum by the biasing force of the spring, and the on-off valve body is closed.

  Thus, conventionally, the pressure control valve body for pressure control during energization and the on-off valve body for flowing liquid to the second passage during non-energization are integrated into a single solenoid for pressure control and passage. Both can be opened and closed. However, if the second passage provided with the passive valve is connected between the pressure control valve body and the on-off valve body in the first passage as in the prior art, the following problems may be pointed out. .

  In the conventional structure, when the flow rate of the first passage increases with the damping force characteristic softened by reducing the amount of current supplied to the solenoid valve, the differential pressure between the upstream and downstream sides of the on-off valve body increases. Thus, the pressure between the on-off valve body and the pressure control valve body increases, and the electromagnetic valve body may be pushed up by the pressure. And if the solenoid valve is pushed up in this way, the on-off valve body may be closed even when it is normal, resulting in a failure state (fail state). If becomes a fail state, the damping force characteristic shifts to the characteristic at the time of failure.

  Such a phenomenon is naturally canceled and returns to a normal state if the flow rate decreases, but until then, the back pressure of the main valve body is dominated by the passive valve, and pressure control by the solenoid valve is not performed. It does not work. For this reason, the damping force cannot be adjusted until the normal state is restored.

  On the other hand, in order to solve the above problem, if the second passage is simply reconnected upstream of the pressure control valve body in the first passage, the valve opening pressure of the passive valve is reduced by opening the pressure control valve body. It must be set higher than the upper limit of the valve pressure. This is because, in the above configuration, if the valve opening pressure of the passive valve is not set higher than the upper limit pressure of the valve opening pressure of the pressure control valve body, the adjustment range of the valve opening pressure of the pressure control valve body becomes narrow and normal. This is because the damping force adjustment range at the time is narrowed. If the setting of the passive valve is restricted in this way, the damping force characteristic at the time of failure cannot be freely set.

  Moreover, the valve body (passive valve body) of the passive valve used for the above-described conventional damping valve is a leaf valve. This leaf valve is a thin annular plate, and is mounted in a state in which bending on the outer peripheral side is allowed. When the outer peripheral portion of the leaf valve is seated on the corresponding valve seat (passive valve valve seat), the second passage is closed. On the other hand, when the leaf valve is bent and the outer peripheral portion is separated from the passive valve seat, the second passage is opened.

  However, when a leaf valve is used as a passive valve body as in the past, the leaf valve and the passive valve seat are in contact with each other, and the leaf valve is attracted to the passive valve seat in the closed state. There is a possibility. When such adsorption occurs, the opening delay of the leaf valve is dynamically observed when the leaf valve is opened, and the pressure in the back pressure chamber may overshoot the opening pressure of the leaf valve for a moment.

  For this reason, when adsorption | suction of a passive valve body occurs, the pressure of a back pressure chamber will change suddenly at the time of the valve opening. Then, since the opening degree of the main flow path of the main valve body also changes suddenly due to the pressure fluctuation in the back pressure chamber, the damping force generated by the shock absorber at the time of failure also changes suddenly. This sudden change in the damping force of the shock absorber causes vibrations in the vehicle body to generate abnormal noise, or deteriorates the riding comfort in the vehicle.

  Furthermore, when a leaf valve is used as the passive valve body, the valve opening pressure of the passive valve can be changed by changing the number of stacked leaf valves or changing the thickness and outer diameter of the leaf valve. The damping force characteristic of can be changed. However, the degree of freedom in selecting the thickness and shape of the leaf valve that can be selected is limited. For this reason, the characteristics of the passive valve cannot be set finely, and it is difficult to finely adjust the damping force characteristics at the time of failure.

  These problems can occur not only when the pressure controlled by the electromagnetic valve is the back pressure of the main valve body, but also when the valve device is used as a damping valve for a shock absorber. Therefore, the present invention was devised to solve such a problem, and even when both the pressure control and the opening / closing of the passage are performed by a solenoid valve, it is prevented from being in a failure state during normal operation. Another object of the present invention is to provide a valve device and a shock absorber that can freely and finely set the characteristics of the passive valve and can suppress the adsorption of the passive valve body.

  A valve device that solves the above problems includes a first passage and a second passage that are connected downstream of a pressure introduction passage, and controls the upstream pressure by opening the first passage when energized, and closes the second passage. The electromagnetic valve which closes a 1st channel | path while energizing and opens a 2nd channel | path, and the passive valve provided downstream from the electromagnetic valve of a 2nd channel | path are provided. The passive valve has a spherical passive valve body that opens and closes the second passage by being attached to and detached from the annular passive valve seat, and a leaf spring that biases the passive valve body in the closing direction.

  According to the above configuration, even when both pressure control and opening and closing of the passage are performed by the electromagnetic valve, the solenoid valve is closed upstream of the passive valve when energized, so that the valve device is in a failed state when it is normal. Can be prevented. Furthermore, since the passage through which the liquid from the pressure introduction passage can pass is switched between when the solenoid valve is energized and when it is not energized, the characteristics of the passive valve can be freely set. Moreover, according to the said structure, a passive valve body can be spherical and can be made into the structure which carries out a line contact with a passive valve valve seat. For this reason, adsorption | suction of a passive valve body can be suppressed. Furthermore, since the shape of the leaf spring can be freely changed, the characteristics of the passive valve can be set finely.

  Further, in the above valve device, the solenoid valve body, which is a valve body of the solenoid valve, opens and closes the first passage and the second passage, and opens and closes the downstream side of the first passage in the first passage. It is preferable that the opening / closing valve body opens the first passage and closes the second passage when the solenoid valve is energized to control the valve opening pressure of the pressure control valve body.

  According to the above configuration, the pressure control valve body for controlling the pressure when energized and the on-off valve body for flowing the liquid to the second passage when not energized are integrated into a single solenoid for pressure control and passage. Even when both opening and closing can be performed, it is possible to prevent the valve device from failing when it is normal and to freely set the passive valve regardless of the valve opening pressure of the pressure control valve body.

  Further, the valve device includes a cylindrical valve case into which an on-off valve body is slidably inserted on the inner peripheral side, and the on-off valve valve in the first passage is positioned at a position shifted in the axial direction of the valve case. A first port serving as an opening / closing portion of the body and a second port serving as an opening / closing portion of the opening / closing valve body in the second passage are formed, and a pressure control valve valve body is provided at an end portion on the first port side of the valve case. There is provided a pressure control valve seat that is attached and detached, and a spring that biases the solenoid valve body in a direction in which the solenoid valve separates the pressure control valve body from the pressure control valve seat, and a biasing force of the spring It is good to have the solenoid which gives the thrust of an opposite direction to a solenoid valve body. According to this configuration, when the solenoid valve is energized, it is easy to control the valve opening pressure of the pressure control valve body by opening the first passage with the on-off valve body and closing the second passage.

  Moreover, in the said valve apparatus, it is good for the passive valve valve seat to be provided in the edge part by the side of the 2nd port of a valve case. According to this configuration, since the valve case and the passive valve seat can be integrated, if they are integrally formed as one part, the number of parts of the valve device can be reduced and the cost can be reduced. Furthermore, since the valve case and the passive valve can be arranged in a compact manner, the valve device can be downsized.

  The valve device has a main passage that communicates between the one chamber and the other chamber, an annular valve seat member that passes through the inner passage on the inner periphery side, and a liquid flow that passes through the main passage after being seated on and off the valve seat member. And a pressure introduction passage that reduces the pressure in the one chamber and guides it to the back surface of the main valve body as a back pressure, and the main valve body is attached to and detached from the valve seat member. The second valve body member has an annular first valve body member and a second valve body member that is stacked on the side opposite to the valve seat member of the first valve body member and seats on and off the first valve body member. A valve case and a passive valve are attached, the first valve body member and the second valve body member are urged away from the valve seat member by the pressure of the one chamber, and the second valve body member is the first valve body member It is good to urge in the direction which leaves | separates from a 1st valve body member with the pressure of the inner peripheral side.

  According to the above configuration, when the pressure in the one chamber increases during normal operation, the resistance by the main valve body can be changed by controlling the back pressure of the main valve body and the thrust of the solenoid. Conversely, when the pressure in the other chamber increases during normal operation, the resistance by the main valve element can be changed by controlling the thrust of the solenoid.

  The shock absorber includes a cylinder, a piston slidably inserted into the cylinder, and the valve device. The valve device provides resistance to a flow of liquid generated when the piston moves in the cylinder. It may be a damping valve.

  According to the above configuration, if the valve device can be prevented from being in a failure state at the normal time as described above, the normal damping force characteristic can be prevented from being a failure characteristic. Furthermore, if the characteristics of the passive valve can be set freely and finely as described above, the damping force characteristics at the time of failure can be set freely and finely. In addition, if the adsorption of the passive valve body can be suppressed as described above, a sudden change in the damping force at the time of failure is suppressed, and when the shock absorber is interposed between the vehicle body and the axle, the vehicle The ride comfort can be improved.

  According to the valve device and the shock absorber of the present invention, even when both pressure control and passage opening / closing are performed with a solenoid valve, it is possible to prevent a failure state during normal operation and to freely set the characteristics of the passive valve. It can be set finely and the adsorption of the passive valve body can be suppressed.

It is a longitudinal cross-sectional view of the shock absorber provided with the damping valve which is a valve apparatus which concerns on one embodiment of this invention. FIG. 2 is an enlarged longitudinal sectional view of a damping valve portion of FIG. 1. It is the longitudinal cross-sectional view which expanded and showed a part of FIG. It is the top view which expanded and showed the leaf | plate spring of the passive valve in the damping valve which is a valve apparatus which concerns on one embodiment of this invention. It is a circuit diagram of an electromagnetic valve of a damping valve which is a valve device concerning one embodiment of the present invention, and a passive valve part.

  Embodiments of the present invention will be described below with reference to the drawings. The same reference numerals used throughout the several drawings indicate the same parts.

  As shown in FIG. 1, the valve device according to one embodiment of the present invention is used as a damping valve V of a shock absorber D. The shock absorber D is used for a vehicle suspension in this embodiment, and includes a cylinder 1, a piston 10 slidably inserted into the cylinder 1, and one end connected to the piston 10 and the other end. Comprises a piston rod 11 projecting out of the cylinder 1.

  The cylinder 1 is connected to one of the vehicle body and the axle of the vehicle, and the piston rod 11 is connected to the other. Thus, the shock absorber D is interposed between the vehicle body and the axle. When the vehicle vibrates up and down, for example, when the vehicle travels on an uneven road surface, the piston rod 11 enters and exits the cylinder 1 and the shock absorber D expands and contracts, and the piston 10 moves up and down in the cylinder 1 in FIG. Move in the axial direction).

  An annular head member 12 that allows the piston rod 11 to be inserted is attached to one end of the cylinder 1 in the axial direction. The head member 12 slidably supports the piston rod 11 and closes one end of the cylinder 1. On the other hand, the other end of the cylinder 1 is closed by a bottom cap 13. In this way, the cylinder 1 is hermetically sealed, and liquid and gas are sealed in the cylinder 1.

  More specifically, a free piston 14 is slidably inserted into the cylinder 1 on the side opposite to the piston rod 11 when viewed from the piston 10. A liquid chamber L filled with a liquid such as hydraulic oil is formed on the piston 10 side of the free piston 14. On the other hand, a gas chamber G in which compressed gas is sealed is formed on the side opposite to the piston 10 when viewed from the free piston 14.

  Thus, in the shock absorber D, the liquid chamber L and the gas chamber G in the cylinder 1 are partitioned by the free piston 14. Furthermore, the liquid chamber L is partitioned by the piston 10 into an extension side chamber L1 on the piston rod 11 side and a pressure side chamber L2 on the opposite side (counter piston rod side). Further, a damping valve V is attached to the piston 10. The damping valve V provides resistance to the flow of liquid that passes between the extension side chamber L1 and the compression side chamber L2.

  According to the above configuration, when the shock absorber D is extended, when the piston 10 moves in the cylinder 1 upward in FIG. 1 and compresses the expansion side chamber L1, the liquid in the expansion side chamber L1 passes through the damping valve V and becomes the compression side chamber L2. And a resistance is given to the liquid flow by the damping valve V. For this reason, when the shock absorber D extends, the pressure in the expansion side chamber L1 rises, and the shock absorber D exerts an expansion-side damping force that prevents the expansion operation.

  On the contrary, when the shock absorber D contracts, the piston 10 moves in the cylinder 1 downward in FIG. 1 to compress the compression side chamber L2, and the liquid in the compression side chamber L2 moves to the expansion side chamber L1 through the damping valve V. At the same time, resistance is given to the flow of the liquid by the damping valve V. For this reason, when the shock absorber D contracts, the pressure in the pressure side chamber L2 increases, and the shock absorber D exerts a pressure-side damping force that prevents the contraction operation.

  Furthermore, when the shock absorber D expands and contracts, the free piston 14 moves to expand or contract the gas chamber G to compensate for the volume of the piston rod 11 entering and exiting the cylinder 1.

  However, the configuration of the shock absorber D is not limited to the illustration and can be changed as appropriate. For example, a reservoir for storing liquid and gas may be provided in place of the gas chamber G, and the liquid may be exchanged between the cylinder and the reservoir when the buffer is extended or contracted. Further, the shock absorber D may be a double rod type, and piston rods may be provided on both sides of the piston. In this case, the configuration for compensating the piston rod volume can be omitted.

  Subsequently, as shown in FIG. 2, the damping valve V includes a main passage P1 communicating with the expansion side chamber L1 and the pressure side chamber L2, an annular valve seat member 2 through which the main passage P1 passes on the inner peripheral side, A main valve body 3 that opens and closes the main passage P1 by being seated on and away from the seat member 2, and a pressure introduction passage P2 that is formed with a throttle O in the middle and reduces the pressure in the extension side chamber L1 to the back of the main valve body 3 The first passage P3 and the second passage P4 connected to the downstream side of the pressure introduction passage P2 (the side opposite to the extension side chamber), the electromagnetic valve 4 for opening and closing the first passage P3 and the second passage P4, A passive valve 5 provided downstream of the electromagnetic valve 4 in the second passage P4, and an expansion side valve 6 and a pressure side valve 7 for opening and closing the pressure side chamber L2 side of the main valve body 3 in the main passage P1 are provided.

  The piston 10 and the piston rod 11 function as a housing H for the damping valve V together with the cylindrical guide 8 that connects them. More specifically, the piston 10 has a bottomed cylindrical shape, and the cylindrical portion 10a faces the piston rod 11 side. The piston rod 11 is provided with a cylindrical case portion 11a at the tip, and this case portion 11a has the cylinder portion 11b facing the piston 10 side. Thus, the piston 10 and the case portion 11a are arranged so that the cylindrical portions 10a and 11b face each other.

  Then, one end portion of the guide 8 in the axial direction is screwed to the inner periphery of the tip end portion of the cylindrical portion 11b in the case portion 11a, and the other end portion in the axial direction of the guide 8 is screwed to the inner periphery of the tip end portion of the cylindrical portion 10a of the piston 10. Has been. In this way, the case portion 11a, the guide 8, and the piston 10 are integrated to function as the housing H of the damping valve V. Inside the housing H, the valve seat member 2, the main valve body 3, the electromagnetic valve 4, and the passive The valve 5 and the pressure side valve 7 are accommodated. Further, the expansion side valve 6 is mounted on the outside of the housing H.

  Hereinafter, each member accommodated in or attached to the housing H in the damping valve V will be described in detail. In the following description, for convenience of description, unless otherwise specified, the upper and lower parts in FIGS. 2 and 3 are simply referred to as “upper” and “lower”.

  A protrusion 10 b is provided on the inner periphery of the cylinder portion 10 a of the piston 10. The outer periphery of the valve seat member 2 is fixed by being sandwiched between the protrusion 10 b and the guide 8. As described above, the valve seat member 2 is annular, and the annular first valve seat 2a is formed on the inner periphery of the upper end thereof. Then, the main valve body 3 is seated on and off from the first valve seat 2a. The main valve body 3 is divided into upper and lower parts, a lower (valve seat member 2 side) first valve body member 30, and an upper second valve body member stacked on the first valve body member 30. 31.

  The 1st valve body member 30 is cyclic | annular, and the cyclic | annular 2nd valve seat 30a in which the 2nd valve body member 31 detaches | separates is formed in the upper end. Furthermore, taper surfaces 30b and 30c are formed on the outer periphery and the inner periphery of the first valve body member 30, respectively. The tapered surfaces 30b and 30c have a truncated cone shape so that the diameter gradually decreases toward the lower end. And the 1st valve body member 30 inserts the part by which the taper surface 30b was formed in the outer periphery to the inner side of the valve seat member 2, and makes the taper surface 30b seat in the 1st valve seat 2a.

  On the other hand, the second valve body member 31 includes a head portion 31a, an annular flange portion 31b connected to the lower side of the head portion 31a and having an outer diameter larger than the outer diameter of the head portion 31a, and a lower end of the flange portion 31b. It has an annular leg portion 31 c that protrudes downward from the inner peripheral portion and is attached to and detached from the second valve seat 30 a, and is slidably inserted inside the guide 8. More specifically, the inner diameter of the guide 8 is larger on the lower side than on the upper side. In the guide 8, if the small inner diameter portion is the small inner diameter portion 8a and the larger portion is the large inner diameter portion 8b, the head portion 31a of the second valve body member 31 is in sliding contact with the inner periphery of the small inner diameter portion 8a, and the large inner diameter portion 8b. The flange portion 31b of the second valve body member 31 is in sliding contact with the inner periphery of the second valve body member 31.

  Subsequently, as shown in FIG. 3, an annular gap K is formed on the outer periphery of the leg portion 31c and the first valve body member 30 of the second valve body member 31 and below the flange portion 31b. The annular gap K communicates with the extension side chamber L1 through a communication hole 8c formed in the guide 8, and the pressure in the annular gap K becomes substantially equal to the pressure of the extension side chamber L1. And the pressure of the extension side chamber L1 acts on the taper surface 30b of the outer peripheral side in the main valve body 3, the lower surface of the flange part 31b, etc., and the 1st valve body member 30 and the 2nd valve body member 31 are extended side chamber L1. It is biased upward by the pressure of.

  More specifically, the outer diameter of the contact portion with the first valve seat 2a on the tapered surface 30b of the first valve body member 30 is the diameter a, and the sliding contact with the large inner diameter portion 8b of the flange portion 31b of the second valve body member 31 is performed. Let the outer diameter of the part be the diameter b. Then, the diameter b is larger than the diameter a (b> a), and the pressure receiving area of the main valve body 3 that receives the pressure of the expansion side chamber L1 is an area obtained by subtracting the area of the circle of the diameter a from the area of the circle of the diameter b. . And the main valve body 3 is urged | biased in the direction (opening direction) which separates the 1st valve body member 30 from the 1st valve seat 2a with the force which multiplied the pressure receiving area to the pressure of the expansion side chamber L1.

  For this reason, when the buffer D is extended, the pressure in the expansion side chamber L1 rises, and when the first valve body member 30 and the second valve body member 31 are pushed up by the pressure and the first valve body member 30 is opened, the expansion side chamber The liquid of L1 passes between the 1st valve body member 30 and the 1st valve seat 2a, and goes to the bottom part 10c (FIG. 2) side of the piston 10. As shown in FIG. And the 1st valve body member 30 gives resistance to the flow of the said liquid.

  As shown in FIG. 2, an extension side passage 10 d and a pressure side passage 10 e are formed in the bottom portion 10 c of the piston 10 so as to penetrate the bottom portion 10 c vertically. That is, between the head portion 31a of the second valve body member 31 and the bottom portion 10c of the piston 10, the flange portion 31b, the leg portion 31c, the first valve body member 30, the valve seat member 2, and the cylinder of the piston 10 are provided. When the inner peripheral side of the portion 10a is a central chamber L3, the extension side passage 10d and the pressure side passage 10e can communicate with the central chamber L3 and the pressure side chamber L2.

  The inlet of the extension side passage 10d is always communicated with the central chamber L3, and the outlet of the extension side passage 10d is opened and closed by the extension side valve 6 stacked below the bottom portion 10c. The expansion side valve 6 is opened when the shock absorber D is extended to provide resistance to the flow of the liquid from the expansion side passage 10d toward the compression side chamber L2 from the central chamber L3, and closes when contracting to flow in the opposite direction. Stop.

  On the other hand, the inlet of the pressure side passage 10e is always in communication with the pressure side chamber L2, and the outlet of the pressure side passage 10e is opened and closed by a pressure side valve 7 stacked on the upper side of the bottom portion 10c. The pressure side valve 7 opens when the shock absorber D is contracted to provide resistance to the flow of the liquid from the pressure side passage 10e toward the central chamber L3 from the pressure side chamber L2 and closes when extended to prevent the flow in the opposite direction. . And the liquid which flowed into the central chamber L3 from the pressure side chamber L2 at the time of shrinkage | contraction of the buffer D heads for the main valve body 3 side.

  The pressure in the central chamber L3 acts on the lower surface of the leg portion 31c in the second valve body member 31 and the second valve body member 31 is biased upward by the pressure in the central chamber L3. Further, the pressure in the central chamber L3 acts on the tapered surface 30c on the inner peripheral side of the first valve body member 30, and the first valve body member 30 is urged downward by the pressure in the central chamber L3. Thus, the 1st valve body member 30 and the 2nd valve body member 31 are urged | biased by the reverse direction with the pressure of the center chamber L3.

  More specifically, the top and bottom of the head portion 31a of the second valve body member 31 are in communication with each other through a vertical hole 31f described later, and these pressures are equal. As shown in FIG. 3, the outer diameter of the sliding contact portion with the small inner diameter portion 8 a in the head portion 31 a of the second valve body member 31 is the diameter c, and the second valve in the leg portion 31 c of the second valve body member 31. The inner diameter of the contact portion with the seat 30a is defined as a diameter d. Then, the diameter d is larger than the diameter c (d> c), and the pressure receiving area of the second valve body member 31 receiving the pressure of the central chamber L3 is an area obtained by subtracting the area of the circle of the diameter c from the area of the circle of the diameter d. It becomes. And the 2nd valve body member 31 is urged | biased in the direction (opening direction) which separates from the 2nd valve seat 30a with the force which multiplied the pressure receiving area to the pressure of the center chamber L3.

  Further, when the inner diameter of the contact portion with the first valve seat 2a in the tapered surface 30b on the outer peripheral side of the first valve body member 30 is a diameter e, the diameter d is larger than the diameter e (d> e), and the central chamber The pressure receiving area of the first valve body member 30 that receives the pressure of L3 is an area obtained by subtracting the area of the circle of the diameter e from the area of the circle of the diameter d. And the 1st valve body member 30 is urged | biased by the direction (closed direction) seated on the 1st valve seat 2a with the force which multiplied the pressure receiving area to the pressure of the center chamber L3.

  For this reason, when the shock absorber D is contracted, the pressure side valve 7 (FIG. 2) is opened, the liquid flows from the pressure side chamber L2 to the central chamber L3, the pressure rises, and the second valve body member 31 is pushed up by this pressure. When the first valve body member 30 is separated from the first valve body member 30, the liquid in the central chamber L3 moves between the second valve body member 31 and the second valve seat 30a and moves to the extension side chamber L1. And the 2nd valve body member 31 gives resistance with respect to the flow of the said liquid.

  As can be seen from the above, the communication hole 8c, the annular gap K, the central chamber L3, the extension side passage 10d and the pressure side passage 10e are part of the main passage P1 that connects the extension side chamber L1 and the pressure side chamber L2. The main passage P1 is opened and closed by the main valve body 3. Further, the pressure side chamber L2 side of the main passage P1 from the opening / closing portion of the main valve body 3 branches into the extension side passage 10d and the pressure side passage 10e, and the extension side valve 6 or the pressure side valve 7 is provided respectively (FIG. 2). ). In other words, the expansion side valve 6 and the pressure side valve 7 are connected in parallel to the pressure side chamber L2 side of the main valve body 3.

  When the shock absorber D is extended, the first valve body member 30 and the expansion side valve 6 provide resistance to the liquid flow from the expansion side chamber L1 to the compression side chamber L2 through the main passage P1, and the shock absorber D is caused by the resistance. Exhibits the damping force on the extending side. On the other hand, when the shock absorber D is contracted, the second valve body member 31 and the pressure side valve 7 provide resistance to the liquid flow from the pressure side chamber L2 to the expansion side chamber L1 through the main passage P1, and the shock absorber D is caused by the resistance. Demonstrate the damping force on the compression side.

  Moreover, in this Embodiment, the notch 31d (FIG. 3) is formed in the lower end of the leg part 31c of the 2nd valve body member 31. As shown in FIG. An orifice is formed by the notch 31d. For this reason, even when the main valve body 3 is closed, that is, when both the first valve body member 30 and the second valve body member 31 are closed, the extension side chamber L1 and the central chamber L3 are connected via the orifice. Communicated.

  Subsequently, an annular back pressure chamber L4 is formed between the head portion 31a of the second valve body member 31 and the large inner diameter portion 8b of the guide 8 and above the flange portion 31b. The back pressure chamber L4 and the extension side chamber L1 are communicated with each other by a pressure introduction passage P2 formed in the guide 8. The pressure introducing passage P2 is provided with a throttle O, so that the pressure in the expansion side chamber L1 is reduced and led to the back pressure chamber L4.

  Then, the pressure in the back pressure chamber L4 rises when the shock absorber D in which the pressure in the expansion side chamber L1 is increased and acts on the upper surface of the flange portion 31b which becomes the back surface of the main valve body 3, and the first valve body member 30 The second valve body member 31 is urged downward by the pressure of the back pressure chamber L4. More specifically, the pressure receiving area of the main valve body 3 that receives the pressure of the back pressure chamber L4 is an area obtained by subtracting the area of the circle of the diameter c (FIG. 3) from the area of the circle of the diameter b (FIG. 3). . And the main valve body 3 makes the 1st valve body member 30 and the 2nd valve body member 31 respectively the 1st valve seat 2a and the 2nd valve seat 30a by the force which multiplied the pressure receiving area to the pressure of the back pressure chamber L4. It is urged in the direction to be seated (closed direction).

  Further, as shown in FIG. 3, the head 31a of the second valve body member 31 is formed on the outer peripheral side of the mounting hole 31e and the mounting hole 31e passing through the center of the head 31a up and down. A vertical hole 31f communicating with the top and bottom of the head 31a and a horizontal hole 31g having one end opened in the back pressure chamber L4 and the other end opened in the mounting hole 31e are formed. Further, a valve case 9 including a first port 9a and a second port 9b is mounted in the mounting hole 31e. The first port 9a and the second port 9b are opened and closed by the electromagnetic valve 4.

  More specifically, the valve case 9 includes a cylindrical guide portion 9c that is arranged with one end in the axial direction facing upward, an annular flange portion 9d that protrudes radially outward from the upper end of the guide portion 9c, An annular pressure control valve seat 9e protruding upward from the upper end of the flange 9d. Thus, the shape of the valve case 9 is substantially cylindrical as a whole.

  The first port 9a and the second port 9b described above are formed so as to penetrate the thickness of the guide portion 9c at positions shifted vertically (in the axial direction) of the guide portion 9c. The first port 9a is located above the second port 9b (on the pressure control valve seat 9e side). Moreover, the outer diameter of the guide part 9c is smaller than the diameter of the attachment hole 31e, and the cyclic | annular space | gap closed up and down was formed in the outer periphery of the guide part 9c. A lateral hole 31g is opened in the annular gap. For this reason, the liquid in the back pressure chamber L4 can flow into the inner peripheral side of the guide portion 9c through the lateral hole 31g and the first port 9a or the second port 9b.

  Subsequently, the electromagnetic valve 4 includes an electromagnetic valve valve body 40 that opens and closes the first port 9a and the second port 9b and is attached to and detached from the pressure control valve seat 9e. The solenoid valve body 40 is slidably inserted into the guide portion 9c of the valve case 9 to open one of the first port 9a and the second port 9b and close the other, The on-off valve body 40a protrudes to the upper side of the valve case 9 and protrudes laterally from the shaft 40b whose outer diameter is smaller than the outer diameter of the on-off valve body 40a and the upper end of the shaft 40b that protrudes outside the valve case 9. A pressure control valve valve body 40c that is attached to and detached from the pressure control valve valve seat 9e, and a spring receiving portion 40d that protrudes further laterally from the pressure control valve valve body 40c.

  Furthermore, the solenoid valve 4 has a spring 41 that urges the solenoid valve body 40 upward, that is, in a direction for separating the pressure control valve body 40c from the pressure control valve seat 9e. The spring 41 may be any spring, but is a coil spring in the present embodiment. The upper end of the spring 41 is supported by a spring receiving portion 40 d of the electromagnetic valve body 40. On the other hand, the lower end of the spring 41 is supported on the outer peripheral side of the pressure control valve seat 9e in the flange portion 9d of the valve case 9. Thus, the spring 41 is interposed between the solenoid valve body 40 and the valve case 9.

  The solenoid valve 4 has a solenoid S that applies thrust to the solenoid valve body 40 downward, that is, in a direction in which the pressure control valve body 40c is seated on the pressure control valve seat 9e. As shown in FIG. 2, the solenoid S is housed in the case portion 11a of the piston rod 11, and a molded stator 44 in which a winding 42 and a harness 43 that energizes the winding 42 are integrated with a molding resin. A tentative cylindrical first fixed iron core 45 fitted to the inner periphery of the mold stator 44, an annular second fixed iron core 46 laminated on the lower end of the mold stator 44, and a first fixed iron core 45, A filler ring 47 interposed between the second fixed iron core 46 and forming a magnetic gap therebetween, and axially movable toward the inner peripheral side of the first fixed iron core 45 and the second fixed iron core 46. A cylindrical movable iron core 48 disposed and a shaft 49 fixed to the inner periphery of the movable iron core 48 and having a tip abutting against the electromagnetic valve body 40 are provided.

  When the winding 42 is excited, the magnetic path is formed so as to pass through the first fixed iron core 45, the movable iron core 48, the second fixed iron core 46, and the case portion 11a. It is sucked toward the iron core 46 side. When the movable iron core 48 is sucked in this way, the electromagnetic valve body 40 is pushed downward by the shaft 49. That is, when energized, the solenoid S applies a thrust force in the direction opposite to the biasing force of the spring 41 to the solenoid valve body 40.

  When the solenoid valve body 40 receives such thrust from the solenoid S, the solenoid valve body 40 advances downward while compressing the spring 41, and the on-off valve body 40a moves to the lower side of the first port 9a. The first port 9a is opened and the second port 9b is closed. When the first port 9a is opened by the on-off valve body 40a, the pressure control valve body 40c is seated on or approaches the pressure control valve seat 9e, and the pressure in the back pressure chamber L4 is passed through the first port 9a. Acting on the lower surface of the pressure control valve body 40c, the electromagnetic valve body 40 is biased upward.

  Therefore, when the solenoid S is energized, the resultant force of the pressure of the back pressure chamber L4 that biases the solenoid valve body 40 upward and the biasing force of the spring 41 biases the solenoid valve valve body 40 downward. When the thrust of the solenoid S is exceeded, the pressure control valve body 40c moves away from the pressure control valve seat 9e. When the pressure control valve body 40c is thus opened, the liquid moves between the pressure control valve body 40c and the pressure control valve valve seat 9e and moves to the upper side of the head 31a, and passes through the vertical hole 31f. Then, the head moves from the upper side of the head 31a to the central chamber L3. The valve opening pressure of the pressure control valve body 40c is proportional to the amount of current supplied to the solenoid S, and the valve opening pressure of the pressure control valve body 40c increases as the supply current amount increases.

  On the other hand, when the energization to the solenoid S is cut off, the solenoid valve body 40 is pushed up to the maximum by the urging force of the spring 41. Then, the on-off valve body 40a moves to the upper side of the second port 9b to open the second port 9b and close the first port 9a. 2 and 3 show the state of the electromagnetic valve body 40 when no power is supplied.

  A passive valve 5 is mounted on the lower side of the valve case 9 in the mounting hole 31e. As shown in FIG. 3, the passive valve 5 is a spherical passive valve valve that opens and closes a lower end of the guide portion 9 c by being seated on an annular passive valve seat 9 f provided at the lower end of the guide portion 9 c in the valve case 9. And a leaf spring 51 that urges the passive valve body 50 in a direction (closing direction) in which the passive valve body 50 is seated on the passive valve seat 9f.

  As shown in FIG. 4, the leaf spring 51 has an annular attachment portion 51 a and a plurality of support portions 51 b protruding from the attachment portion 51 a toward the center side. These support parts 51b are arrange | positioned at equal intervals in the circumferential direction of the attaching part 51a. The plate spring 51 is configured such that the mounting portion 51a is fixed to the second valve body member 31, and the lower end of the passive valve valve body 50 is supported by the tip of the support portion 51b.

  When the solenoid S, which opens the second port 9b by the on-off valve body 40a, is de-energized, the pressure in the back pressure chamber L4 acts on the upper side surface of the passive valve body 50 through the second port 9b. The valve body 50 is biased downward, that is, in a direction in which the passive valve body 50 is separated from the passive valve valve seat 9f. Therefore, when the solenoid S is not energized, the liquid in the back pressure chamber L4 flows into the lower side of the on-off valve body 40a from the second port 9b, and the passive valve body 50 is moved against the urging force of the leaf spring 51. When pushed down, it moves to the central chamber L3 between the passive valve body 50 and the passive valve valve seat 9f and between the adjacent support portions 51b and 51b.

  As can be seen from the above, the first port 9a, the upper side of the head portion 31a, and the vertical hole 31f are part of the first passage P3 connected to the downstream side of the pressure introduction passage P2. When the solenoid S is energized, the on-off valve body 40a opens the first port 9a, connects the first passage P3 and the back pressure chamber L4, and controls the valve opening pressure of the pressure control valve body 40c. For this reason, when the solenoid valve 4 is energized when the shock absorber D in which the pressure in the back pressure chamber L4 increases, the pressure in the back pressure chamber L4 is controlled to the valve opening pressure of the pressure control valve body 40c. .

  On the other hand, the lower side of the valve case 9 in the second port 9b and the mounting hole 31e is a part of the second passage P4 connected downstream of the pressure introduction passage P2. When the solenoid S is not energized, the on-off valve body 40a opens the second port 9b and connects the second passage P4 and the back pressure chamber L4. A passive valve 5 is provided in the second passage P4. For this reason, when energization to the electromagnetic valve 4 is interrupted when the shock absorber D in which the pressure in the back pressure chamber L4 increases, the pressure in the back pressure chamber L4 becomes the valve opening pressure of the passive valve 5.

  As described above, the pressure in the back pressure chamber L4 acts in the direction in which the main valve body 3 is closed. In addition, when the solenoid valve 4 is energized, the thrust of the solenoid S also acts in the direction of closing the main valve body 3 via the solenoid valve valve body 40 and the valve case 9. For this reason, when the shock absorber D expands when the solenoid valve 4 is energized normally, the force due to the pressure of the expansion side chamber L1 that biases the first valve body member 30 of the main valve body 3 in the opening direction is the main valve body. When the force resulting from the pressure of the back pressure chamber L4 energizing 3 in the closing direction exceeds the resultant force of the solenoid S, the first valve body member 30 opens.

  When the shock absorber D is extended in a normal state, adjusting the thrust of the solenoid S and controlling the pressure of the back pressure chamber L4 with the electromagnetic valve 4 adjusts the force for energizing the main valve body 3 in the closing direction. And the resistance by the 1st valve body member 30 provided to the flow of the liquid which goes through the main channel | path P1 from the expansion side chamber L1 to the center chamber L3 is changed. For this reason, at the time of normality, the damping force (extension side damping force) when the shock absorber D is extended can be adjusted.

  Specifically, if the amount of current supplied to the solenoid valve 4 is increased, the thrust of the solenoid S increases and the pressure of the back pressure chamber L4 increases during extension, and the force that biases the main valve body 3 in the closing direction is increased. Since it becomes large, the damping force characteristic can be made hard by increasing the damping force on the extension side. On the other hand, if the amount of current supplied to the solenoid valve 4 is reduced, the thrust of the solenoid S becomes small and the pressure in the back pressure chamber L4 becomes low at the time of extension, and the force for energizing the main valve body 3 in the closing direction becomes small. Therefore, the damping force characteristic can be made soft by reducing the damping force on the extension side.

  On the other hand, when the shock absorber D extends during a failure in which the power supply to the electromagnetic valve 4 is cut off, the pressure in the back pressure chamber L4 becomes the valve opening pressure of the passive valve 5. For this reason, the extension side damping force at the time of failure is determined by the setting of the passive valve 5. Further, since the communication between the second passage P4 provided with the passive valve 5 and the back pressure chamber L4 is cut off at the normal time, the damping force characteristic of the shock absorber D becomes the characteristic at the time of the failure despite the normal time. There is no.

  When the shock absorber D is contracted so that the pressure in the back pressure chamber L4 does not increase, the pressure control valve body 40c does not open even if the first port 9a is open, and the pressure control of the back pressure chamber L4 by the electromagnetic valve 4 is effective. Disappear. However, during energization, the thrust of the solenoid S acts in the direction of closing the main valve body 3 via the electromagnetic valve body 40 and the valve case 9. For this reason, if the thrust of the solenoid S is adjusted, the resistance by the second valve body member 31 applied to the liquid flow from the central chamber L3 toward the extension side chamber L1 through the main passage P1 is changed. The damping force at the time of contraction of D (the damping force on the compression side) can also be adjusted.

  Specifically, when the amount of current supplied to the solenoid valve 4 is increased, the thrust of the solenoid S is increased even during contraction, and the force that biases the main valve body 3 in the closing direction is increased. The damping force characteristic can be made hard by increasing the value. On the other hand, if the amount of current supplied to the solenoid valve 4 is reduced, the thrust of the solenoid S is reduced even during contraction, and the force that biases the main valve body 3 in the closing direction is reduced, so the damping force on the compression side is reduced. The damping force characteristics can be softened.

  On the other hand, when the solenoid S is not energized, the solenoid valve body 40 is retracted to the maximum by receiving the urging force of the spring 41. At this time, the main valve body 3 is only urged together with the valve case 9 by the spring 41 in the closing direction. For this reason, the damping force on the pressure side of the shock absorber D becomes the smallest during a failure, and the damping force characteristic becomes full soft.

  Hereinafter, the effect of the damping valve V which is the valve device according to the present embodiment will be described.

  In the present embodiment, the damping valve (valve device) V includes the pressure introduction passage P2, the first passage P3 and the second passage P4 connected downstream of the pressure introduction passage P2, and the first passage P3 when energized. Open and control the upstream pressure, close the second passage P4, close the first passage P3 when not energized and open the second passage P4, and downstream of the electromagnetic valve 4 in the second passage P4 And a passive valve 5 provided. Then, the passive valve 5 is separated from and seated on the annular passive valve seat 9f so as to open and close the second passage P4, and a leaf spring for biasing the passive valve body 50 in the closing direction. 51.

  According to the above configuration, even when both pressure control and passage opening / closing are performed by the electromagnetic valve 4, the upstream side of the passive valve 5 is closed by the electromagnetic valve 4 when energized, so that the damping valve (valve device) V Can be prevented from failing during normal operation. Furthermore, since the passage through which the liquid from the pressure introduction passage P2 can pass is switched between when the solenoid valve 4 is energized and when it is not energized, the characteristics of the passive valve 5 can be freely set.

  Moreover, according to the said structure, the passive valve body 50 can be spherical and can be made into the structure which carries out line contact with the passive valve valve seat 9f. For this reason, adsorption | suction of the passive valve body 50 can be suppressed. Furthermore, the leaf | plate spring 51 can change the board | plate thickness, the number of the support parts 51b, length, the width | variety of the circumferential direction, etc. freely. Thus, since the shape of the leaf | plate spring 51 can be changed freely, the characteristic of the passive valve 5 can be set finely. In addition, since the passive valve body 50 is spherical, for example, if the passive valve body 50 is dropped on the passive valve valve seat 9f, it is naturally aligned. For this reason, according to the said structure, the assembly of the passive valve 5 can be made easy.

  Further, in the damping valve (valve device) V of the present embodiment, as shown in FIG. 4, the solenoid valve body 40 that is the valve body of the solenoid valve 4 opens and closes the first passage P3 and the second passage P4. It includes a valve body 40a and a pressure control valve body 40c that opens and closes the downstream side of the opening / closing valve body 40a in the first passage P3. When the solenoid valve 4 is energized, the on-off valve body 40a opens the first passage P3 and closes the second passage P4, and the valve opening pressure of the pressure control valve body 40c is controlled.

  According to the electromagnetic valve 4, the upstream pressure can be controlled to the valve opening pressure of the pressure control valve body 40c when energized. In the solenoid valve 4, the on-off valve body 40a of the solenoid valve body 40 opens and closes the upstream side of the pressure control valve body 40c. That is, it is not configured to open and close the downstream side of the pressure control valve body with the opening and closing valve body as in the prior art. Therefore, even when the on-off valve body 40a and the pressure control valve body 40c are integrated and driven by a single solenoid S, both pressure control and passage opening / closing are performed by the electromagnetic valve 4, It is possible to prevent the damping valve (valve device) V from failing when it is normal.

  In addition, when the energization is performed when the passive valve 5 is functioning, the first passage P3 is closed by the on-off valve body 40a so that the pressure control valve body 40c is not activated, and when the pressure control valve body 40c is activated, the second passage is activated. Passage P4 is closed and passive valve 5 does not function. Therefore, even when the on-off valve body 40a and the pressure control valve body 40c are integrated and driven by a single solenoid S, both pressure control and passage opening / closing are performed by the electromagnetic valve 4, It is not necessary to set the passive valve 5 in consideration of the valve opening pressure of the pressure control valve body 40c, and the characteristics of the passive valve 5 can be freely set.

  In the present embodiment, the valve device according to the present invention is used as the damping valve V of the shock absorber D, and provides resistance to the liquid flow generated when the piston 10 moves in the cylinder 1. For this reason, the shock absorber D can exhibit a damping force due to the resistance of the damping valve V.

  When the solenoid valve 4 is energized, the damping force can be increased or decreased by increasing or decreasing the valve opening pressure of the pressure control valve body 40c. For this reason, as described above, if the damping valve (valve device) V is prevented from failing when it is normal, the damping force characteristic becomes the characteristic at the time of failure regardless of the normal state, and the damping force is not adjusted. Can be prevented.

  Further, the damping force characteristic at the time of failure is determined by the setting of the passive valve 5. Therefore, as described above, if the characteristic of the passive valve 5 can be set freely and finely, the damping force characteristic at the time of failure can be set freely and finely. In addition, as described above, when the adsorption of the passive valve body 50 is suppressed, a sudden change in the damping force at the time of failure is suppressed, and the shock absorber D is interposed between the vehicle body and the axle. The ride comfort of the vehicle can be improved.

  Further, the damping valve (valve device) V of the present embodiment includes a cylindrical valve case 9 into which the on-off valve body 40a is slidably inserted on the inner peripheral side. Then, at a position shifted in the axial direction of the valve case 9, a first port 9a serving as an opening / closing portion of the opening / closing valve body 40a in the first passage P3, and an opening / closing portion of the opening / closing valve body 40a in the second passage P4, A second port 9b is formed.

  Further, a pressure control valve valve seat 9e to which the pressure control valve body 40c is attached and detached is provided at the end of the valve case 9 on the first port 9a side. The solenoid valve 4 has a spring 41 that biases the solenoid valve body 40 in a direction to separate the pressure control valve body 40c and the pressure control valve seat 9e, and a thrust in a direction opposite to the biasing force of the spring 41. A solenoid S provided to the solenoid valve body 40.

  According to the above configuration, when the solenoid valve 4 is energized, it is easy to control the valve opening pressure of the pressure control valve body 40c by opening the first passage P3 with the on-off valve body 40a and closing the second passage P4. . Furthermore, according to the said structure, it is also easy to open the 2nd channel | path P4 while closing the 1st channel | path P3 with the on-off valve body 40a when the solenoid valve 4 is not energized.

  However, the configuration of the solenoid valve 4 is not limited to the above, and the first passage P3 is opened to control the upstream pressure when energized, the second passage P4 is closed, and the first passage P3 is closed when not energized. As long as the 2nd channel | path P4 is opened, it can change suitably.

  In the present embodiment, the passive valve seat 9 f is provided at the end of the valve case 9 on the second port 9 b side. According to this configuration, since the valve case 9 and the passive valve seat 9f can be integrated, if these are integrally formed as one part, the number of parts of the damping valve (valve device) V can be reduced and the cost can be reduced.

  Furthermore, according to the above configuration, since the valve case 9 and the passive valve 5 can be installed in a compact manner, when the valve case 9 and the passive valve 5 are mounted on the main valve body 3 like the damping valve V of the present embodiment. The main valve body 3 is not bulky, and the damping valve (valve device) V can be downsized. However, the passive valve valve seat 9f may be provided separately from the valve case 9. Such a change is possible regardless of the configuration of the electromagnetic valve 4.

  Further, the damping valve (valve device) V of the present embodiment includes a main passage P1 communicating with the expansion side chamber L1 and the pressure side chamber L2, an annular valve seat member 2 through which the main passage P1 passes on the inner peripheral side, And a main valve body 3 that is separated from and seated on the valve seat member 2 and provides resistance to the flow of liquid passing through the main passage P1. Then, the pressure in the extension side chamber L1 is reduced by the pressure introduction passage P2 and guided to the back surface of the main valve body 3 as a back pressure.

  Further, the main valve body 3 is laminated on the first valve body member 30 by being laminated on the annular valve body member 30 that is separated from the valve seat member 2 and on the counter valve seat member side of the first valve body member 30. The second valve body member 31 that is separated and seated is provided, and the valve case 9 and the passive valve 5 are attached to the second valve body member 31. And the 1st valve body member 30 and the 2nd valve body member 31 are urged | biased in the direction which leaves | separates from the valve seat member 2 with the pressure of the expansion side chamber L1. On the other hand, the second valve body member 31 is biased in a direction away from the first valve body member 30 by the pressure on the inner peripheral side of the first valve body member 30.

  According to the above configuration, when the electromagnetic valve 4 is energized, if the shock absorber D extends and the pressure in the expansion chamber L1 increases, the back pressure of the main valve body 3 is reduced to the valve opening pressure of the pressure control valve body 40c. By controlling the back pressure and the thrust force of the solenoid S, it is possible to change the resistance by the first valve body member 30 applied to the liquid flow from the expansion side chamber L1 to the pressure side chamber L2 through the main passage P1.

  Further, when the electromagnetic valve 4 is energized, when the shock absorber D contracts and the pressure in the compression side chamber L2 increases, the thrust of the solenoid S is controlled to move the main passage P1 from the compression side chamber L2 to the expansion side chamber L1. The resistance by the second valve body member 31 applied to the liquid flow can be changed.

  On the other hand, when the shock absorber D expands and the pressure in the expansion side chamber L1 increases when the solenoid valve 4 is not energized, the back pressure of the main valve body 3 is determined by the setting of the passive valve 5, so that the passive valve 5 The resistance by the first valve body member 30 can be determined by the setting. Further, when the shock absorber D contracts and the pressure in the pressure side chamber L2 increases when the solenoid valve 4 is not energized, the resistance of the second valve body member 31 can be determined by the setting of the spring 41.

  In the present embodiment, the one chamber and the other chamber communicated by the main passage P1 are the extension side chamber L1 and the pressure side chamber L2 of the shock absorber D, respectively. However, the room communicated by the main passage P1 is not necessarily limited to the extension side chamber L1 and the compression side chamber L2. For example, as described above, when the shock absorber includes a reservoir, the main passage P1 may be a passage communicating the extension side chamber or the pressure side chamber and the reservoir.

  Furthermore, in the present embodiment, when the pressure in the expansion side chamber L1 is guided to the back pressure chamber L4 through the pressure introduction passage P2, and the shock absorber D expands in a normal state, the back pressure of the main valve body 3 is increased. Is controlled by the valve opening pressure of the pressure control valve body 40c. However, the pressure on the upstream side of the main valve body 3 in the main passage P1 may be guided to the back pressure chamber L4 both when the shock absorber D is extended and contracted.

  The valve device according to the present invention does not necessarily include the main passage P1 and the main valve body 3. Further, in the present embodiment, the expansion side valve 6 and the pressure side valve 7 are connected in parallel to the pressure side chamber L2 side of the main valve body 3 in the main passage P1, but these may be eliminated. In addition, the use of the valve device according to the present invention is not limited to the damping valve of the shock absorber D, and can be changed as appropriate. These changes can be made regardless of the configuration of the electromagnetic valve 4 and the configuration of the passive valve 5.

  The preferred embodiments of the present invention have been described above in detail, but modifications, changes and modifications can be made without departing from the scope of the claims.

D ... shock absorber, L1 ... extension side chamber (one chamber), L2 ... pressure side chamber (other chamber), P1 ... main passage, P2 ... pressure introduction passage, P3 ... first Passage, P4 ... second passage, S ... solenoid, V ... damping valve (valve device), 1 ... cylinder, 2 ... valve seat member, 3 ... main valve body, 4 ... Solenoid valve, 5 ... Passive valve, 9 ... Valve case, 9a ... First port, 9b ... Second port, 9e ... Pressure control valve valve seat, 9f ... Passive valve seat, 10 ... piston, 30 ... first valve body member, 31 ... second valve body member, 40 ... solenoid valve body, 40a ... open / close valve body, 40c ... Pressure control valve disc, 41 ... Spring, 50 ... Passive valve disc, 51 ... Leaf spring

Claims (6)

A pressure introduction passage;
A first passage and a second passage connected downstream of the pressure introduction passage;
An electromagnetic valve that opens the first passage when energized and controls the pressure on the upstream side and closes the second passage; closes the first passage and closes the second passage when not energized; and
A passive valve provided downstream of the electromagnetic valve of the second passage,
The passive valve includes a spherical passive valve body that opens and closes the second passage by being attached to and detached from an annular passive valve valve seat, and a leaf spring that biases the passive valve body in a closing direction. A characteristic valve device. The solenoid valve includes an on-off valve valve body that opens and closes the first passage and the second passage, and a pressure control valve body that opens and closes a downstream side of the on-off valve body in the first passage. Having a disc,
The open / close valve body opens the first passage and closes the second passage when the solenoid valve is energized, and the valve opening pressure of the pressure control valve body is controlled. The valve device as described. A cylindrical valve case in which the on-off valve body is slidably inserted on the inner peripheral side,
A first port serving as an opening / closing portion of the on-off valve valve body in the first passage and a second port serving as an opening / closing portion of the on-off valve valve body in the second passage at positions shifted in the axial direction of the valve case. Is formed,
A pressure control valve valve seat on which the pressure control valve body is detached is provided at an end portion on the first port side of the valve case,
The solenoid valve includes a spring that biases the solenoid valve body in a direction that separates the pressure control valve body and the pressure control valve valve seat, and a thrust in a direction opposite to the biasing force of the spring. The valve device according to claim 2, further comprising a solenoid provided to the valve body. The valve device according to claim 3, wherein the passive valve seat is provided at an end portion of the valve case on a second port side. A main passage communicating between the one chamber and the other chamber;
An annular valve seat member through which the main passage passes on the inner peripheral side;
A main valve body that is separated from and seated on the valve seat member and gives resistance to a flow of liquid passing through the main passage,
The pressure introducing passage is for reducing the pressure in the one chamber and introducing it as a back pressure to the back surface of the main valve body,
The main valve body is an annular first valve body member that is attached to and detached from the valve seat member; A dual valve body member,
The valve case and the passive valve are attached to the second valve body member,
The first valve body member and the second valve body member are urged in a direction away from the valve seat member by the pressure of the one chamber,
5. The valve device according to claim 3, wherein the second valve body member is biased in a direction away from the first valve body member by a pressure on an inner peripheral side of the first valve body member. . A cylinder,
A piston slidably inserted into the cylinder;
A valve device according to any one of claims 1 to 5,
The said valve | bulb apparatus gives resistance to the flow of the liquid produced when the said piston moves in the said cylinder. The shock absorber characterized by the above-mentioned.

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