WO2013122252A1 - Shock absorber - Google Patents

Shock absorber Download PDF

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Publication number
WO2013122252A1
WO2013122252A1 PCT/JP2013/053846 JP2013053846W WO2013122252A1 WO 2013122252 A1 WO2013122252 A1 WO 2013122252A1 JP 2013053846 W JP2013053846 W JP 2013053846W WO 2013122252 A1 WO2013122252 A1 WO 2013122252A1
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WO
WIPO (PCT)
Prior art keywords
valve body
working fluid
port
damping force
fluid chamber
Prior art date
Application number
PCT/JP2013/053846
Other languages
French (fr)
Japanese (ja)
Inventor
福田　博美
Original Assignee
ヤマハ発動機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by ヤマハ発動機株式会社 filed Critical ヤマハ発動機株式会社
Publication of WO2013122252A1 publication Critical patent/WO2013122252A1/en

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
    • B60G17/06—Characteristics of dampers, e.g. mechanical dampers
    • B60G17/08—Characteristics of fluid dampers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/44—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction
    • F16F9/46—Means on or in the damper for manual or non-automatic adjustment; such means combined with temperature correction allowing control from a distance, i.e. location of means for control input being remote from site of valves, e.g. on damper external wall
    • F16F9/464—Control of valve bias or pre-stress, e.g. electromagnetically
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
    • B60G2202/20—Type of damper
    • B60G2202/24—Fluid damper

Definitions

  • the present invention relates to a shock absorber.
  • a motor vehicle, a motorcycle and the like are provided with a shock absorber (shock absorber) in order to attenuate vibrations generated in the vehicle.
  • the shock absorber usually comprises a cylinder, in which a piston and a support shaft for supporting the piston are provided.
  • the inside of the cylinder is separated into two oil chambers by the piston, and the piston moves according to the expansion and contraction of the shock absorber, whereby the oil moves between the two oil chambers.
  • the oil movement path is provided with an orifice, valve, etc. with a relatively narrow flow passage area as a damping force generation part, and the damping force is generated by the fluid resistance when passing through these narrow flow passages. Dampen the vibrations generated by the vehicle.
  • shock absorber As a conventional shock absorber, there is a shock absorber provided with a damping force control valve (variable orifice) whose opening degree can be adjusted by electronic control.
  • damping force control valve variable orifice
  • shock absorbers there are a shock absorber in which the valve is installed in the cylinder and a shock absorber in which the valve is installed outside the cylinder. In either case, the main damping force generating portion
  • the damping force control valve is installed in the bypass to the valve, and the damping force can be controlled by adjusting the opening degree of the damping force control valve according to the traveling conditions.
  • FIG. 7 is a longitudinal sectional view schematically showing a shock absorber 401 shown in Patent Document 1.
  • FIG. 7 (a) shows the shock absorber 401 at the time of the hard characteristic (at the time of full closing),
  • FIG. 7 (b) These show the shock absorber 401 at the time of a soft characteristic (refer FIG. 1 of patent document 1).
  • the shock absorber 401 comprises a cylinder 402 with a piston 403.
  • the space in the cylinder 402 is divided by the piston 403 into an upper cylinder chamber 402 a and a lower cylinder chamber 402 b.
  • the piston 403 is provided with main fluid passages 407 and 408.
  • Damping force generators 409 and 410 are provided in the main fluid passages 407 and 408, respectively.
  • the bypass 412 is provided with a damping force generator 413 and a check valve 414.
  • the flow path resistance of the damping force generating portion 413 is smaller than that of the damping force generating portions 409 and 410 of the main fluid passages 407 and 408.
  • a cylindrical guide member 415 having an opening 416 is installed in the bypass 412.
  • a shutter-shaped valve body 417 is provided inside the guide member 415.
  • the valve body 417 is provided with passages 419 and 420.
  • the valve body 417 is disposed on the rod 423.
  • the rod 423 is supported by the support member 421 and linearly reciprocates by the solenoid actuator 424.
  • damping force control in the bypass 412 is performed by adjusting the flow passage area of the bypass 412.
  • the valve body 417 has a shutter shape, the range of controllable flow rate in the bypass 412 (the minimum value and the maximum value of the area of the communicating portion between the opening 416 and the passage 419 In order to widen the difference with the value, it is necessary to secure a wide area in which the valve body 417 and the guide member 415 are opposed in the radial direction. Therefore, the radial dimension of the valve body 417 can not but be increased.
  • the rod 423 connecting the solenoid actuator 424 and the valve body 417 protrudes from the support member 421 so that the valve body 417 shuts off the oil passage (bypass 412).
  • the spring 422 needs to be further strengthened, and the size of the solenoid actuator 424 is further increased.
  • the installation space of the valve as much as possible because the installation space of the equipment is limited.
  • the demand for weight reduction of the valve is also very strong. Therefore, enlargement of the valve should be avoided as much as possible.
  • the present invention has been made in view of the above-described problems, and while ensuring good running performance even when the current can not be supplied, a wide range of small and controllable flow rates can be secured. It is to provide a shock absorber.
  • the present invention adopts the following configuration in order to solve the problems described above.
  • a shock absorber is A damping force generating unit that generates damping force by fluid resistance of the working fluid; And a damping force control valve disposed in a bypass to the damping force generation unit,
  • the damping force control valve is A valve body linearly reciprocated by a solenoid;
  • a first working fluid chamber including a guide hole through which the valve body is inserted, and a port formed at a position facing the end face of the valve body;
  • a second working fluid chamber in which an end opposite to the end face of the valve body is exposed;
  • An urging body that applies a force to the valve body along an axial direction of the valve body; And a passage communicating the first working fluid chamber with the second working fluid chamber.
  • a gap between the end face of the valve body and the port is a flow passage through which the working fluid passes,
  • the opening degree of the flow passage is changed by the position of the end face of the valve body, whereby the damping force is controlled,
  • the valve body is separated from the port, and when the solenoid is not energized, the biasing body causes a force toward the port along the axial direction of the valve body by the biasing body. , Added to the valve body, thereby moving the valve body to the closed position.
  • the end face of the valve body and the port face each other, and the gap between the end face of the valve body and the port is a flow path through which the working fluid passes.
  • the degree of opening of the flow path is changed by the position of the end face of the valve body that linearly reciprocates in the axial direction, whereby the damping force is controlled.
  • the amount of change in the flow passage area with respect to the stroke (displacement in the axial direction) of the valve body is large. Therefore, a wide controllable flow rate range can be secured in the bypass without increasing the diameter of the valve body.
  • the distance between the end face of the opposite valve body and the port is a flow path through which the working fluid passes, so when adjusting the position of the end face of the valve body, the inside of the valve body and the first working fluid chamber It does not slide with the wall. Therefore, the increase in friction due to sliding can be avoided. In addition, since a sliding portion does not occur around the flow path through which the working fluid passes, the increase in friction due to the entrapment of minute foreign matter does not occur.
  • the flow of the working fluid in the first working fluid chamber is discharged to the outside of the first working fluid chamber through the port.
  • the pressure difference between the downstream end of the valve body and the opposite end of the downstream end is small based on the direction. Therefore, generation of a pressure difference between the first working fluid chamber and the second working fluid chamber can be suppressed. Therefore, there is no need to strengthen the biasing body as in the shock absorber shown in FIG. The enlargement of the solenoid can be avoided.
  • the biasing body applies a force to the valve disc toward the port along the axial direction of the valve disc.
  • the valve disc pushes away the working fluid in the first working fluid chamber and moves toward the port, but the pressure at that time propagates to the second working fluid chamber 40 through the passage, so the first working fluid
  • the increase in pressure in the room can be suppressed.
  • the increase in friction during movement of the valve body is prevented. Therefore, the gap between the end face of the valve body and the port can be quickly closed only by the biasing force of the biasing body.
  • the shock absorber of (1) can ensure a wide range of compact and controllable flow rates while securing good running performance even when the current can not be supplied.
  • the shock absorber of (1) The passage is provided along the axial direction of the valve body, and the first working fluid chamber and the second operation are operated when the solenoid is not energized and the space between the valve body and the port becomes narrow.
  • the fluid chambers it is preferable to reduce the pressure difference between the two working fluid chambers by flowing the working fluid from the working fluid chamber on the high pressure side to the working fluid chamber on the low pressure side.
  • the passage communicating the first working fluid chamber and the second working fluid chamber is relatively short. Therefore, when the space between the end face of the valve body and the port (flow path of the working fluid) is closed, pressure transmission between the first working fluid chamber and the second working fluid chamber occurs rapidly. Thereby, the generation of the pressure difference between the first working fluid chamber and the second working fluid chamber can be suppressed more effectively. Therefore, responsiveness can be further enhanced.
  • the passage connecting the first working fluid chamber and the second working fluid chamber is further shortened, and the passage approaches the port when the distance between the valve body and the port narrows. Responsiveness can be improved.
  • the passage since the passage is provided in the valve body, the space for forming the passage may not be secured outside the valve. Therefore, enlargement of the valve can be avoided.
  • the biasing body is installed in the first working fluid chamber and applies a force to the valve body in the axial direction of the valve body toward the port.
  • the valve body can be smoothly moved by pulling the valve body to the first working fluid chamber side by the biasing body, so that the positional stability of the valve body and Responsiveness is further improved.
  • the shock absorber according to any one of (1) to (4),
  • the biasing body is disposed at a position where a part of the biasing body overlaps the passage in the axial direction of the valve body, and the valve body is directed to the port along the axial direction of the valve body with respect to the valve body It is preferable to apply force.
  • the damping force control valve can be miniaturized.
  • the shock absorber according to any one of (1) to (4), The biasing body is disposed at a position where all of the biasing body overlaps the passage in the axial direction of the valve body, and a force directed to the port along the axial direction of the valve body with respect to the valve body
  • the damping force control valve can be further miniaturized.
  • FIG. 1 is a longitudinal sectional view schematically showing a damping force control valve 10 provided in a shock absorber 100 according to the present invention.
  • FIG. 1 shows the closed state of the damping force control valve 10 when it is not energized.
  • the direction in which the working fluid of the first working fluid chamber 30 is discharged through the first port 30a is referred to as the downstream direction D.
  • a direction opposite to the downstream direction D along the axial direction S of the valve body 20 is referred to as an opposite direction U.
  • the damping force control valve 10 includes a hollow cylindrical outer cylinder 11 (housing).
  • the outer cylinder 11 includes an opening 11 a on the downstream direction D side and an opening 11 b on the opposite direction U side.
  • the inner cylinder 12 is fitted into the opening 11 b of the outer cylinder 11.
  • the opposite direction U side end of the outer cylinder 11 is bent inward and abuts against the inner cylinder 12 in the axial direction S, whereby the outer cylinder 11 and the inner cylinder 12 are fixed.
  • the outer cylinder 11 has a flange portion 11 c that annularly protrudes toward the axial center at a substantially central portion in the axial direction S.
  • the flange portion 11c has a cylindrical portion 11d extending toward the opening 11b at its inner edge.
  • the cylindrical guide member 13 is inserted into the cylindrical portion 11 d.
  • the guide member 13 has a flange portion 13a on the downstream direction D side.
  • the flanges 11c and 13a are in contact with each other. Thereby, in the outer cylinder 11, the movement to the opposite direction U side of the guide member 13 is regulated.
  • the guide member 13 is provided with a guide hole 13b.
  • a hollow cylindrical valve body 20 is slidably inserted into the guide hole 13b.
  • the valve body 20 has an end face 20a on the downstream direction D side and an end face 20b on the opposite direction U side.
  • the valve body 20 is formed with a passage 21 extending from the end face 20a to the end face 20b.
  • the passage 21 includes a large diameter portion 21 a including an end surface 20 a on the downstream direction D side, and a communication portion 21 b extending toward the second working fluid chamber 40 from the opposite direction U side end of the large diameter portion 21 a.
  • the communicating portion 21 b is a columnar space, and the diameter is substantially constant.
  • the opening area of the passage 21 (large diameter part 21a) at the end face 20a on the downstream direction D side of the valve body 20 is larger than the opening area of the communication part 21b.
  • the diameter of the communication portion 21b is the smallest. That is, in the damping force control valve 10, the communication portion 21b is the smallest diameter portion in the passage 21.
  • the boundary between the large diameter portion 21 a and the communication portion 21 b in the axial direction S is located in the first working fluid chamber 30.
  • the end face 20 a on the downstream direction D side of the valve body 20 faces the first port 30 a of the first working fluid chamber 30.
  • the end surface 20a does not abut on the wall surface (bottom surface 26a) of the first working fluid chamber 30.
  • the valve body 20 is made of a nonmagnetic material.
  • a hollow cylindrical support member 14 is installed on the opposite direction U side of the cylindrical portion 11 d.
  • the support member 14 faces the cylindrical portion 11 d coaxially with the cylindrical portion 11 d.
  • the supporting member 14 has an opening 14a formed on the downstream direction D side, an opening 14b formed on the opposite direction U side, and a guide portion 14c which annularly protrudes toward the axial center at a substantially central portion in the axial direction S Have.
  • An annular bearing 20c is installed on the inner peripheral side of the guide portion 14c.
  • the valve body 20 is inserted into the bearing 20c, and the bearing 20c slidably supports the valve body 20.
  • a spring receiving member 15 is fixed on the inner peripheral surface of the support member 14 closer to the opening 14 b than the guide portion 14 c.
  • An annular seal 16 (e.g., an O-ring) for sealing between the support member 14 and the spring receiving member 15 is provided on the outer peripheral surface of the spring receiving member 15.
  • a cap 17 is provided at the opposite direction U side end of the support member 14. The cap 17 closes the opening 14 b.
  • a second working fluid chamber 40 is formed between the guide portion 14 c and the spring receiving member 15.
  • the end face 20 b of the valve body 20 is exposed in the second working fluid chamber 40.
  • the coil spring 18 is supported by the end face 20 b of the valve body 20 and the spring receiving member 15.
  • the coil spring 18 biases the valve body 20 in the downstream direction D.
  • a cylindrical cylindrical member 19 is provided to connect the cylindrical portion 11 d and the support member 14.
  • the cylindrical member 19 is made of a nonmagnetic material.
  • a bobbin 22 is provided in the outer cylinder 11, a bobbin 22 is provided.
  • the bobbin 22 covers the outer peripheral surface of the support member 14 and the outer peripheral surface of the cylindrical member 19.
  • a solenoid coil 23 is wound around the bobbin 22.
  • An annular plate-like cap 24 is attached between the bobbin 22 and the inner cylinder 12 on the inner peripheral surface of the outer cylinder 11.
  • the cap 24 is made of a magnetic material (for example, iron).
  • a cylindrical plunger 25 is fixed between the guide member 13 and the guide portion 14c.
  • the inner diameter of the cylindrical portion 11 d is larger than the outer diameter of the plunger 25.
  • the inner diameter of the portion closer to the opening 14 a than the guide portion 14 c is larger than the outer diameter of the plunger 25. Therefore, the plunger 25 can move in the axial direction S between the guide member 13 and the guide portion 14c.
  • the damping force control valve 10 by adjusting the magnetic flux density of the magnetic field generated by the solenoid coil 23, the plunger 25 can be moved in the axial direction S between the guide member 13 and the guide portion 14c. Thereby, the valve body 20 moves in the axial direction S.
  • the solenoid coil 23 and the coil spring 18 constitute a solenoid.
  • the installation space 25 a of the plunger 25 is formed by the cylindrical portion 11 d, the guide member 13, the guide portion 14 c and the cylindrical member 19.
  • the working fluid HO is also filled in the installation space 25a.
  • the space 25 a communicates with the first working fluid chamber 30 via a gap between the outer peripheral surface of the valve body 20 and the inner peripheral surface of the guide member 13.
  • the space 25 a communicates with the second working fluid chamber 40 through a gap between the outer peripheral surface of the valve body 20 and the inner peripheral surface of the guide portion 14 c.
  • a substantially cylindrical valve head 26 with a bottom is disposed on the side of the opening 11 a in the outer cylinder 11 so as to contact the flange portion 13 a of the guide member 13.
  • a first port 30 a is formed at the center of the bottom surface 26 a of the valve head 26.
  • the first port 30 a is installed at a position facing the end face 20 a of the valve body 20.
  • the working fluid path 31 extends from the first port 30a in the downstream direction D.
  • the valve head 26 is provided with a second port 30 b on the outer peripheral wall 26 c of the valve head 26.
  • the working fluid passage 32 extends radially from the second port 30b.
  • a first working fluid chamber 30 is constituted by the valve head 26 and the guide member 13.
  • the first working fluid chamber 30 is provided with a guide hole 13 b.
  • the first working fluid chamber 30 and the second working fluid chamber 40 are disposed opposite to each other with the valve body 20 interposed therebetween.
  • the end face 20 a of the valve body 20 is disposed on the first working fluid chamber 30 side.
  • the first working fluid chamber 30 and the second working fluid chamber 40 are in communication via the passage 21 of the valve body 20.
  • a space in the first working fluid chamber 30 is located around the outer peripheral surface of the valve body 20. The working fluid flows from the working fluid passage 32 along the radial direction of the valve body 20 into the first working fluid chamber 30.
  • the guide hole 13b and the first port 30a are formed at mutually opposing positions across the space in the first working fluid chamber 30.
  • the distance between the guide hole 13b and the first port 30a is longer than the distance between the first port 30a and the second port 30b.
  • the distance between the guide hole 13b and the second port 30b is longer than the distance between the first port 30a and the second port 30b.
  • the second port 30b is closer to the first port 30a than the guide hole 13b.
  • the second port 30 b is provided between the guide hole 13 b and the first port 30 a.
  • no member that slides on the valve body 20 is provided.
  • the guide hole 13b and the valve body 20 slide, but the portion where the guide hole 13b and the valve body 20 slide is provided at a position separated from the first port 30a and the second port 30b. Therefore, it is possible to suppress an increase in friction due to minute foreign matter.
  • a circlip 33 as a fixture is fixed to the outer periphery of the valve body 20.
  • a fixing tool is not limited to a circlip.
  • a coil spring 34 as a biasing body is installed between the circlip 33 and the bottom surface 26 a of the valve head 26 on the downstream direction D side of the circlip 33.
  • the valve body 20 is inserted into the coil spring 34.
  • the diameter of the coil spring 34 increases. Therefore, the flow of the working fluid from the working fluid passage 32 to the working fluid passage 31 via the first working fluid chamber 30 is less likely to be blocked by the coil spring 34.
  • a coil spring 35 as an urging body is installed between the circlip 33 and the downstream side surface 13c of the guide member 13 on the opposite direction U side of the circlip 33 as a fixing tool.
  • the valve body 20 is inserted through the coil spring 35. As the reverse direction U is approached, the diameter of the coil spring 35 increases.
  • an urging body is not limited to a coil spring,
  • conventionally well-known urging bodies such as a leaf
  • FIG. 2 is a longitudinal sectional view schematically showing the damping force control valve shown in FIG. 1 in an open state (a), a minute open state (b) and a closed state (c).
  • the damping force control valve 10 a part (approximately half) of the end face 20a (see FIG. 1) of the valve body 20 is subjected to slant processing.
  • the end face 20a includes the flat portion 20d and the inclined portion 20e which is inclined in the opposite direction D from the flat portion 20d.
  • FIG. 2B shows the valve body 20 moving in the downstream direction D.
  • the flat portion 20d of the end face 20a of the valve body 20 has an axis. In the direction S, it exists at the same position as the first port 30a. There is a space between the slope 20e and the first port 30a. This interval is the flow path T of the working fluid. Since the large diameter portion 21a is formed in the valve body 20, when part of the working fluid that has passed through the flow path T of the working fluid flows in the opposite direction U, it forms a vortex and diffuses in the large diameter portion 21a. It becomes easy to go to the downstream direction D. Therefore, the generation of the pressure difference between the first working fluid chamber 30 and the second working fluid chamber 40 can be suppressed more efficiently.
  • the flow path T is a part of the outer peripheral edge of the valve body 20 and the first It is a distance from a part of the outer peripheral edge of one port 30a. Therefore, the change in the opening area of the flow passage T with respect to the stroke (displacement amount in the axial direction S) of the valve body 20 is relatively small.
  • the valve body 20 is further moved in the downstream direction D from the state shown in FIG. 2B by the coil springs 18, 34, 35, and stops at the position shown in FIG. 2C.
  • This position is the closed position of the valve body 20.
  • the closed position is the position on the most downstream direction D side where the valve body 20 is moved by the coil springs 18, 34, 35 when the solenoid coil 23 is not energized.
  • the first port 30 a is preferably closed by the valve body 20. In other words, it is preferable that the first port 30 a be substantially fully closed by the valve body 20 when the valve body 20 is in the closed position.
  • the term "substantially fully closed state” as used herein means that a case where a slight amount of opening occurs depending on the use state or the like is allowed.
  • the first port 30 a may be completely closed by the valve body 20.
  • the downstream direction D side end of the passage 21 enters the first port 30a, and the passage 21 communicates with the working fluid chamber 31.
  • FIG. 3 is a longitudinal sectional view schematically showing an open state (a), a minute open state (b) and a closed state (c) of a damping force control valve according to another embodiment of the present invention.
  • 3 is the same as FIG. 2 except for the shape of the downstream end D side end of the valve body 20, in FIG. 3, the same reference numerals are given to the same configuration as FIG. Omit or simplify.
  • the end face 20 a ′ on the downstream direction D side of the valve body 20 is flat.
  • the solenoid coil 23 is deenergized in the state shown in FIG. 3A
  • the valve body 20 moves in the downstream direction D.
  • the damping force control valve 10 becomes a minute opening degree.
  • the flow path T is the distance between the entire outer peripheral edge of the valve body 20 and the fully open peripheral edge of the first port 30a.
  • the valve body 20 is further moved in the downstream direction D, and as shown in FIG. 3C, the end face 20a 'of the valve body 20 and the first port 30a exist at the same position in the axial direction S.
  • the end face 20a 'of the body 20 closes the first port 30a.
  • the end face 20a 'of the valve body 20 is located at the closed position.
  • FIG. 4 is a longitudinal sectional view schematically showing an open state (a), a minute opening degree state (b) and a closed state (c) of a damping force control valve according to another embodiment of the present invention.
  • 4 is the same as FIG. 2 except for the shape of the downstream direction D side end of the valve body 20, in FIG. 4 the same reference numerals are given to the same configuration as FIG. , Omit or simplify the explanation.
  • the valve body 20 includes the passage 21 penetrating the valve body 20 in the axial direction S, but the large diameter portion 21 a is not formed.
  • the valve body 20 is provided with an annular end surface 20 a ′ ′.
  • the end face 20a '' of the valve body 20 and the first port 30a exist at the same position in the axial direction S,
  • the end face 20a 'of the valve body 20 closes the first port 30a.
  • the end face 20a 'of the valve body 20 is located at the closed position.
  • 5 and 6 are hydraulic circuit diagrams showing a shock absorber 100 provided with the damping force control valve 10 shown in FIG.
  • the shock absorber 100 is provided with a hydraulic cylinder 112.
  • a piston assembly 144 is installed in the hydraulic cylinder 112 in the hydraulic cylinder 112 .
  • the hydraulic cylinder 112 is divided into two working fluid chambers 158 and 160 by a piston assembly 144.
  • One end of the piston rod 162 is inserted into the hydraulic cylinder 112 from one end side of the hydraulic cylinder 112 and is fixed to the piston assembly 144.
  • the other end of the piston rod 162 is connected to the vehicle body side (not shown) of the vehicle.
  • the other end of the hydraulic cylinder 112 is connected to the wheel side (not shown) of the vehicle body.
  • the piston assembly 144 as a damping force generator includes damping valves 148 and 150 with a plurality of shims.
  • the damping valve 148 can flow the working fluid from the working fluid chamber 160 to the working fluid chamber 158, at which time a damping force is generated (elongation damping).
  • the working fluid can not flow in the opposite direction.
  • the damping valve 150 can flow the working fluid from the working fluid chamber 158 to the working fluid chamber 160, at which time a damping force is generated (shrinkage damping).
  • the working fluid can not flow in the opposite direction.
  • a damping force adjustment device 116 is installed between the working fluid chamber 158 and the reservoir tank 114.
  • the damping force control valve 10 a damping valve 116b having a plurality of shims, and a check valve 116c are installed in parallel.
  • the damping valve 116 b can flow the working fluid from the hydraulic cylinder 112 side to the reservoir tank 114 side, and can not flow the working fluid in the opposite direction.
  • the check valve 116 c can flow the working fluid from the reservoir tank 114 side to the hydraulic cylinder 112 side.
  • the working fluid can not flow in the opposite direction.
  • the working fluid O and the gas G are contained in the reservoir tank 114, and the working fluid O and the gas G are in contact at the interface OS.
  • the working fluid O is, for example, working oil or the like.
  • the gas G is, for example, nitrogen gas or air.
  • the damping force control valve 10 in the state shown in FIGS. 2 (a) and 2 (b), 3 (a) and 3 (b), and FIGS. 4 (a) and 4 (b), the working fluid It is possible to flow from 32 to the working fluid passage 31 via the first working fluid chamber 30.
  • the damping force control valve 10 can also flow in the opposite direction. Further, as shown in FIGS. 5 and 6, the damping force control valve 10 is installed as a bypass for the damping valve 116b.
  • the resistance when flowing through the damping force adjusting device 116 increases the pressure of the working fluid in the hydraulic cylinder 112 and resists the movement of the piston rod 162 in the X1 direction (cylinder The pressure of the working fluid (cross sectional area of the piston rod 162), that is, the compression damping force (1) is generated.
  • the opening degree of the damping force control valve 10 is adjusted, the ratio of the flow rate between the damping valve 116 b and the damping force control valve 10 changes, so that the resistance of the damping valve 116 is adjusted and the compression acting on the piston rod 162 Damping force is adjusted.
  • the working fluid flows from the working fluid chamber 158 toward the working fluid chamber 160 also in the damping valve 150 of the piston assembly 144, and the resistance at that time acts on the piston assembly 144 and the compression damping force (2) on the piston rod 162 Is added as
  • the shock absorber 100 when the piston assembly 144 moves in the X2 direction, as shown in FIG. 6, the working fluid of the volume from which the piston rod 162 is withdrawn passes through the check valve 116 c without resistance and returns to the hydraulic cylinder 112.
  • the damping force control valve 10 part of the damping force at the time of compression can be adjusted by the damping force control valve 10.
  • the compression damping force (1) generated by the approach of the piston rod 162 in the damping forces during compression ie, the above-mentioned compression damping forces (1) and (2)
  • the shock absorber 100 may be capable of adjusting all of the damping force at the time of compression by the damping force control valve 10.
  • a check valve may be provided to flow the working fluid from the working fluid chamber 158 to the working fluid chamber 160.
  • the shock absorber 100 configured as described above, when the piston assembly 144 moves in the X1 direction, the above-described compression damping force (1) is generated, but the above-described compression damping force (2) is not generated. Therefore, by adjusting the compression damping force (1), it is possible to adjust all of the damping forces at the time of compression.
  • the end face 20a of the valve body 20 and the first port 30a face each other, and the gap between the entire outer peripheral edge of the end face 20a of the valve body 20 and the entire outer peripheral edge of the first port 30a is , Flow path T of the working fluid.
  • the opening degree of the flow path T is changed by the position of the end face 20a of the valve body 20, whereby the damping force is controlled. Since the amount of change in the flow passage area with respect to the stroke of the valve body 20 is large, a wide controllable flow rate range can be secured in the bypass with respect to the damping valve 116b as the damping force generating portion without increasing the diameter of the valve body 20.
  • the distance between the end face 20a of the valve body 20 and the first port 30a is the flow path T of the working fluid, so when adjusting the position of the end face 20a of the valve body 20, The inner wall surface of the working fluid chamber 30 does not slide. Therefore, the increase in friction due to sliding can be avoided. In addition, since a sliding portion does not occur around the flow path T of the working fluid, an increase in friction due to entrapment of minute foreign matter does not occur.
  • first working fluid chamber 30 and the second working fluid chamber 40 communicate with each other through the passage 21 of the valve body 20, the end face 20a on the downstream direction D side of the valve body 20 and the opposite direction U side The pressure difference with the end face 20b is small. Therefore, the generation of the pressure difference between the first working fluid chamber 30 and the second working fluid chamber 40 can be suppressed. As a result, enlargement of the solenoid can be avoided.
  • the coil springs 18, 34, 35 apply a force to the valve body 20 toward the first port 30a along the axial direction of the valve body 20.
  • the valve body 20 displaces the working fluid in the first working fluid chamber 30 and moves toward the first port 30 a, but the pressure at that time propagates to the second working fluid chamber 40 via the passage 21.
  • the pressure increase of the first working fluid chamber 30 is suppressed.
  • the sliding movement between the valve body 20 and the other members does not occur in the first working fluid chamber 30, an increase in friction during movement of the valve body 20 is prevented.
  • the gap between the end face 20a of the valve body 20 and the first port 30a can be quickly closed only by the biasing force of the coil springs 18, 34, 35.
  • the responsiveness at the time of non-energization of the solenoid is excellent. Can quickly obtain hard characteristics. Therefore, the shock absorber 100 can ensure a wide range of small and controllable flow rates while securing good traveling performance even when the current can not be supplied.
  • the passage 21 penetrates the valve body 20 along the axial direction of the valve body 20, the passage 21 is short. Therefore, when the solenoid coil 23 can not be energized and the distance between the valve body 20 and the first port 30a becomes narrow, the pressure difference between the first working fluid chamber 30 on the high pressure side and the second working fluid chamber 40 on the low pressure side It can be made smaller quickly and has excellent responsiveness. Further, since the passage 21 is provided in the valve body 20, the space for forming the passage 21 may not be secured outside the valve body 20. Therefore, enlargement of the valve can be avoided.
  • the coil spring 34, 35 is disposed in the first working fluid chamber 30, and in order to apply a force toward the first port 30a along the axial direction of the valve body 20 to the valve body 20, One working fluid chamber 30 can be smoothly pulled out.
  • the coils 34 and 35 are disposed at positions where the coils 34 and 35 overlap the passage 21 in the axial direction S of the valve body 20, and the first port along the axial direction S of the valve body 20 with respect to the valve body 20. Add force towards 30a. Therefore, since the coil springs 34 and 35 and the valve body 20 can be disposed more compactly, the damping force control valve 10 can be further miniaturized.
  • the arrangement method of a damping force adjustment device is not limited to the above-mentioned example.
  • the shock absorber 100 shown in FIGS. 5 and 6 is configured to allow the working fluid to flow in both directions with respect to the damping force control valve 10, the present invention is not limited to this example.
  • the working fluid can be made to flow in a direction in which the working fluid is discharged from at least the first working fluid chamber 30 via the first port 30a.
  • the shock absorber 100 may be configured to flow the working fluid in a direction to discharge the working fluid from the first working fluid chamber 30 via the first port 30a at the time of extension, and at the time of retraction, the first working fluid chamber 30 may be configured to flow the working fluid in the direction of discharging the working fluid via the first port 30a.
  • a damping force adjustment device 116 is installed between the hydraulic cylinder 112 and the reservoir tank 114, and a check valve 116c as a damping force generation unit for generating a contraction damping force is provided in the damping force adjustment device 116.
  • the damping force control valve 10 is installed in the bypass for the damping valve 116b. At the time of retraction, in the damping force adjustment device 116, the working fluid of the volume of the piston rod 162 entering the hydraulic cylinder 112 flows. A portion of the working fluid flows through the damping valve 116 b, and the remaining portion of the working fluid flows through the damping force control valve 10.
  • the damping valve 116 b and the damping force control valve 10 are in a bypass relationship with each other.
  • the present invention is not limited to this example.
  • a damping valve as a damping force generation unit may be installed in the shock absorber 100.
  • the damping force control valve 10 is installed in the bypass to the check valve 116c that generates the stretching damping force.
  • the damping force adjustment device 116 the working fluid flows by the volume of the piston rod 162 which is withdrawn from the inside of the hydraulic cylinder 112. A portion of the working fluid flows through the damping valve, and the remaining portion of the working fluid flows through the damping force control valve 10.
  • the damping valve and the damping force control valve 10 are in a bypass relationship with each other.
  • the damping force control valve 10 may be installed outside the hydraulic cylinder 112 in a bypass for the damping force generating portion (the damping valve 116b) that generates the contraction damping force. It may be installed in the bypass for the damping force generating part to generate, and may be installed in both bypasses.
  • damping force control valve 10 may be installed in a bypass to damping valve 150 in hydraulic cylinder 112. At the time of retraction, in the damping valve 150, the working fluid of the volume reduction of the working fluid chamber 158 flows. A portion of the working fluid flows through the damping valve 150, and the remaining portion of the working fluid flows through the damping force control valve 10. At this time, the damping valve 150 and the damping force control valve 10 are in a bypass relationship with each other. Furthermore, damping force control valve 10 may be installed in a bypass to damping valve 150 in hydraulic cylinder 112. At the time of extension, at the damping valve 148, the working fluid of the volume reduction of the working fluid chamber 160 flows. A portion of the working fluid flows through the damping valve 148, and the remaining portion of the working fluid flows through the damping force control valve 10. At this time, the damping valve 148 and the damping force control valve 10 are in a bypass relationship with each other.
  • the damping force control valve 10 may be installed in the hydraulic cylinder 112 in a bypass to the damping force generating portion (damping valve 150) that generates the contraction damping force. It may be placed in a bypass for the damping force generating part (damping valve 148) to be generated, or it may be placed in both bypasses.
  • the damping force control valve 10 may be installed in a bypass for the damping force generation unit, and the installation position and the installation mode of the damping force control valve 10 are not particularly limited.
  • the passage 21 penetrates the valve body 20 in the axial direction S.
  • the formation position of the passage 21 is not limited to this example.
  • the passage may be formed on the outer peripheral side surface of the valve body 20 along the axial direction S.
  • the passage may not be formed in the valve body 20.
  • the passage may be formed in a member facing the outer peripheral side surface of the valve body 20 along the axial direction S.
  • coil springs 34 and 35 as biasing members are installed in the first working fluid chamber 30.
  • the coil spring 35 is an urging body that applies a force toward the first port 30 a to the valve body 20 when it is extended.
  • the coil spring 34 is an urging body that applies a force toward the first port 30 a to the valve body 20 during retraction. In the present invention, any one of these two biasing members may be provided.
  • valve body shape of a valve body is not limited to the above-mentioned example.
  • the valve body may have a hollow rectangular tube shape.
  • shape of the oil passage is not limited to the above example, and the cross section of the oil passage may be polygonal or elliptical.
  • a proportional solenoid is used as the solenoid has been described.
  • the present invention is not limited to this example, and an ON / OFF solenoid may be used as the solenoid, for example.
  • damping force control valve 20 valve body 21 passage 21a large diameter portion 21b communicating portion 23 solenoid coil 26 valve bed 30 first working fluid chamber 30a first port 40 second working fluid chamber 100 shock absorber

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Abstract

Provided is a shock absorber for which a large damping force is set when electrification is impossible. A damping force control valve (10) is arranged in a bypass of a damping force generator in a shock absorber (100). The damping force control valve (10) comprises a valve element (20) that reciprocates due to a solenoid (23), a first operating fluid chamber (30) provided with a port (30a), a second operating fluid chamber (40) that communicates with a channel (21), and a coil spring (35). The valve element (20) moves further away from the port (30a) and the volume of an attenuating medium flowing in the bypass increases in correspondence to a larger electrification amount on the solenoid (23). The valve element (20) moves to a position to block the port (30a) when the solenoid (23) is not electrified since a force on the valve element (20) toward the port (30a) is provided by the coil spring (35).

Description

ショックアブソーバshock absorber
　本発明は、ショックアブソーバに関する。 The present invention relates to a shock absorber.
　一般に、自動車および自動二輪車等には、車両において発生する振動を減衰するためにショックアブソーバ（緩衝器）が設けられている。ショックアブソーバは、通常、シリンダを備え、シリンダ内に、ピストンと、ピストンを支持する支持軸とが設けられている。シリンダ内は、ピストンによって、２つのオイル室に分離されており、ショックアブソーバの伸縮に合わせてピストンが動き、これにより、２つのオイル室の間でオイルが移動する。オイルの移動経路には、減衰力発生部として、比較的流路面積の狭いオリフィス、バルブ等が設けられており、これらの面積の狭い流路を通過するときの流体抵抗により、減衰力を発生させ、車両に発生する振動を減衰させる。 In general, a motor vehicle, a motorcycle and the like are provided with a shock absorber (shock absorber) in order to attenuate vibrations generated in the vehicle. The shock absorber usually comprises a cylinder, in which a piston and a support shaft for supporting the piston are provided. The inside of the cylinder is separated into two oil chambers by the piston, and the piston moves according to the expansion and contraction of the shock absorber, whereby the oil moves between the two oil chambers. The oil movement path is provided with an orifice, valve, etc. with a relatively narrow flow passage area as a damping force generation part, and the damping force is generated by the fluid resistance when passing through these narrow flow passages. Dampen the vibrations generated by the vehicle.
　従来のショックアブソーバとして、電子制御により開度の調整が可能な減衰力制御弁（可変オリフィス）を備えたショックアブソーバが存在する。このようなショックアブソーバとしては、バルブがシリンダ内に設置されたショックアブソーバと、バルブがシリンダ外に設置されたショックアブソーバとが存在するが、いずれの場合であっても、主としての減衰力発生部に対するバイパス中に減衰力制御弁が設置され、走行条件に応じて減衰力制御弁の開度を調整することにより、減衰力を制御することができる。 As a conventional shock absorber, there is a shock absorber provided with a damping force control valve (variable orifice) whose opening degree can be adjusted by electronic control. As such shock absorbers, there are a shock absorber in which the valve is installed in the cylinder and a shock absorber in which the valve is installed outside the cylinder. In either case, the main damping force generating portion The damping force control valve is installed in the bypass to the valve, and the damping force can be controlled by adjusting the opening degree of the damping force control valve according to the traveling conditions.
　従来の減衰力制御弁としては、ソレノイドを用いた流量制御弁で、断線等により通電不能となった場合には、弁が閉じてハード特性となり、良好な走行性能を確保しようとする弁がある（例えば、特許文献１参照）。 As a conventional damping force control valve, there is a flow control valve using a solenoid, and when it becomes impossible to energize due to disconnection etc., the valve is closed and it has a hard property, and there is a valve to try to secure good running performance. (See, for example, Patent Document 1).
　図７は、特許文献１に示すショックアブソーバ４０１を模式的に示す縦断面図であり、図７（ａ）は、ハード特性時（全閉時）のショックアブソーバ４０１を示し、図７（ｂ）は、ソフト特性時のショックアブソーバ４０１を示す（特許文献１の図１参照）。 FIG. 7 is a longitudinal sectional view schematically showing a shock absorber 401 shown in Patent Document 1. FIG. 7 (a) shows the shock absorber 401 at the time of the hard characteristic (at the time of full closing), FIG. 7 (b) These show the shock absorber 401 at the time of a soft characteristic (refer FIG. 1 of patent document 1).
　ショックアブソーバ４０１は、ピストン４０３を有するシリンダ４０２を備えている。シリンダ４０２内の空間は、ピストン４０３により、シリンダ上室４０２ａと、シリンダ下室４０２ｂとに分けられている。ピストン４０３には、主油液通路４０７、４０８が設けられている。主油液通路４０７、４０８には、減衰力発生部４０９、４１０が設けられている。一方、バイパス４１２には、減衰力発生部４１３と逆止弁４１４とが設けられている。減衰力発生部４１３の流路抵抗は、主油液通路４０７、４０８の減衰力発生部４０９、４１０よりも小さい。 The shock absorber 401 comprises a cylinder 402 with a piston 403. The space in the cylinder 402 is divided by the piston 403 into an upper cylinder chamber 402 a and a lower cylinder chamber 402 b. The piston 403 is provided with main fluid passages 407 and 408. Damping force generators 409 and 410 are provided in the main fluid passages 407 and 408, respectively. On the other hand, the bypass 412 is provided with a damping force generator 413 and a check valve 414. The flow path resistance of the damping force generating portion 413 is smaller than that of the damping force generating portions 409 and 410 of the main fluid passages 407 and 408.
　バイパス４１２には、開口部４１６を備えた筒状のガイド部材４１５が設置されている。ガイド部材４１５の内側に、シャッタ形状の弁体４１７が設けられている。弁体４１７には、通路４１９、４２０が設けられている。弁体４１７は、ロッド４２３に設置されている。ロッド４２３は、支持部材４２１に支持され、ソレノイドアクチュエータ４２４によって直線往復動する。これにより、開口部４１６と通路４１９との流路の開度が調整される。つまり、バイパス４１２における減衰力制御は、バイパス４１２の流路面積の調整により行われる。 In the bypass 412, a cylindrical guide member 415 having an opening 416 is installed. Inside the guide member 415, a shutter-shaped valve body 417 is provided. The valve body 417 is provided with passages 419 and 420. The valve body 417 is disposed on the rod 423. The rod 423 is supported by the support member 421 and linearly reciprocates by the solenoid actuator 424. Thus, the opening degree of the flow path between the opening 416 and the passage 419 is adjusted. That is, damping force control in the bypass 412 is performed by adjusting the flow passage area of the bypass 412.
　図７（ａ）では、弁体４１７によりバイパス４１２が全閉となるので、減衰力特性がハード特性となる。一方、図７（ｂ）では、弁体４１７によりバイパス４１２が開くので、減衰力特性がソフト特性となる。非通電時には、バイパス４１２が全閉となる。 In FIG. 7A, since the bypass 412 is fully closed by the valve body 417, the damping force characteristic is a hard characteristic. On the other hand, in FIG. 7B, since the bypass 412 is opened by the valve body 417, the damping force characteristic becomes a soft characteristic. When not energized, the bypass 412 is fully closed.
特許第３０６００７８号公報Patent No. 3060078
　図７に示すショックアブソーバ４０１では、弁体４１７が、シャッタ形状を有しているので、バイパス４１２において制御可能な流量の範囲（開口部４１６と通路４１９との連通部分の面積の最小値と最大値との差）を広くするためには、弁体４１７とガイド部材４１５とが径方向に対向する面積を広く確保する必要がある。そのため、弁体４１７の径方向寸法を大きくせざるを得ない。 In the shock absorber 401 shown in FIG. 7, since the valve body 417 has a shutter shape, the range of controllable flow rate in the bypass 412 (the minimum value and the maximum value of the area of the communicating portion between the opening 416 and the passage 419 In order to widen the difference with the value, it is necessary to secure a wide area in which the valve body 417 and the guide member 415 are opposed in the radial direction. Therefore, the radial dimension of the valve body 417 can not but be increased.
　そうすると、ガイド部材４１５と弁体４１７との摺動部分Ｆの面積が大きくなり、摩擦が大きくなる。しかも、広くなった摺動部分Ｆが油の流れの中に位置しているので、微小な異物が摺動部分に入り込み、更に摩擦が大きくなる。摩擦の増大への対応として弁体４１７が閉じる方向へ付勢するためのバネ４２２を強くする必要が生じる。バネ４２２が強くなると、弁体４１７を駆動するためのソレノイドアクチュエータ４２４も大型化してしまう。 Then, the area of the sliding portion F between the guide member 415 and the valve body 417 is increased, and the friction is increased. In addition, since the wide sliding portion F is positioned in the flow of oil, minute foreign matter gets into the sliding portion and the friction further increases. It is necessary to strengthen the spring 422 for biasing the valve body 417 in the closing direction in response to the increase in friction. When the spring 422 becomes strong, the solenoid actuator 424 for driving the valve body 417 also becomes large.
　また、通電不能となった際に、弁体４１７が油路（バイパス４１２）を遮断するために、ソレノイドアクチュエータ４２４と弁体４１７とを繋いでいるロッド４２３が支持部材４２１から突出する。このときに弁体４１７周囲の油圧が高いと、ロッド４２３の突出する動きが妨げられる。そこで、ロッド４２３の突出する動きがこの油圧に打ち勝つためには、更にバネ４２２を強くする必要があり、更にソレノイドアクチュエータ４２４の大型化を伴う。自動二輪車や自動車等の車両の分野では、機器の設置スペースが限られているので、弁の設置スペースをなるべく小さくしたいという要請が極めて強い。また、走行性能の向上の観点から、弁の軽量化の要請も非常に強い。従って、弁の大型化は極力避けなければならない。 Further, when the current can not be supplied, the rod 423 connecting the solenoid actuator 424 and the valve body 417 protrudes from the support member 421 so that the valve body 417 shuts off the oil passage (bypass 412). At this time, if the oil pressure around the valve body 417 is high, the projecting motion of the rod 423 is hindered. Therefore, in order for the projecting motion of the rod 423 to overcome the hydraulic pressure, the spring 422 needs to be further strengthened, and the size of the solenoid actuator 424 is further increased. In the field of vehicles such as motorcycles and automobiles, there is a strong demand for reducing the installation space of the valve as much as possible because the installation space of the equipment is limited. In addition, from the viewpoint of improvement of running performance, the demand for weight reduction of the valve is also very strong. Therefore, enlargement of the valve should be avoided as much as possible.
本発明は、上述した課題に鑑みてなされたものであり、通電不能となった場合にも良好な走行性能を確保する構成としながら、小型であり、且つ制御可能な流量の範囲を広く確保できるショックアブソーバを提供することである。 The present invention has been made in view of the above-described problems, and while ensuring good running performance even when the current can not be supplied, a wide range of small and controllable flow rates can be secured. It is to provide a shock absorber.
　本発明は、上述した課題を解決するために、以下の構成を採用する。
　（１）　ショックアブソーバであって、
　前記ショックアブソーバは、
作動流体の流体抵抗により減衰力を発生させる減衰力発生部と、
前記減衰力発生部に対するバイパス中に配置された減衰力制御弁と
を備え、
　前記減衰力制御弁は、
ソレノイドにより直線往復動する弁体と、
前記弁体が挿通されるガイド孔と、前記弁体の端面と対向する位置に形成されたポートとを備えた第一作動流体室と、
前記弁体の前記端面の反対側の端部が露出している第二作動流体室と、
前記弁体の軸線方向に沿って前記弁体に力を加える付勢体と、
前記第一作動流体室と前記第二作動流体室とを連通する通路と
を備え、
　前記弁体の前記端面と前記ポートとの間隙は、作動流体が通過する流路であり、
　前記流路の開度は、前記弁体の前記端面の位置によって変更され、これにより減衰力が制御され、
　前記流路の開度が最大になるとき、前記弁体は前記ポートから離れる一方、前記ソレノイドの非通電時に、前記付勢体により、前記弁体の軸線方向に沿って前記ポートに向かう力が、前記弁体に加えられ、これにより、前記弁体が閉位置に移動する。 The present invention adopts the following configuration in order to solve the problems described above.
(1) A shock absorber,
The shock absorber is
A damping force generating unit that generates damping force by fluid resistance of the working fluid;
And a damping force control valve disposed in a bypass to the damping force generation unit,
The damping force control valve is
A valve body linearly reciprocated by a solenoid;
A first working fluid chamber including a guide hole through which the valve body is inserted, and a port formed at a position facing the end face of the valve body;
A second working fluid chamber in which an end opposite to the end face of the valve body is exposed;
An urging body that applies a force to the valve body along an axial direction of the valve body;
And a passage communicating the first working fluid chamber with the second working fluid chamber.
A gap between the end face of the valve body and the port is a flow passage through which the working fluid passes,
The opening degree of the flow passage is changed by the position of the end face of the valve body, whereby the damping force is controlled,
When the opening degree of the flow path is maximized, the valve body is separated from the port, and when the solenoid is not energized, the biasing body causes a force toward the port along the axial direction of the valve body by the biasing body. , Added to the valve body, thereby moving the valve body to the closed position.
　（１）の構成によれば、弁体の端面とポートとが対向しており、弁体の端面とポートとの間隙が、作動流体が通過する流路である。流路の開度は、軸方向に直線往復動する弁体の端面の位置によって変更され、これにより減衰力が制御される。図７に示すショックアブソーバと異なり、弁体のストローク（軸方向の変位）に対する流路面積の変化量が大きい。従って、弁体の径を大きくすることなく、バイパスにおいて制御可能な流量の範囲を広く確保できる。 According to the configuration of (1), the end face of the valve body and the port face each other, and the gap between the end face of the valve body and the port is a flow path through which the working fluid passes. The degree of opening of the flow path is changed by the position of the end face of the valve body that linearly reciprocates in the axial direction, whereby the damping force is controlled. Unlike the shock absorber shown in FIG. 7, the amount of change in the flow passage area with respect to the stroke (displacement in the axial direction) of the valve body is large. Therefore, a wide controllable flow rate range can be secured in the bypass without increasing the diameter of the valve body.
　また、第一作動流体室において、対向する弁体の端面とポートとの間隔が、作動流体の通過する流路なので、弁体の端面の位置調整時に、弁体と第一作動流体室の内壁面とが摺動しない。従って、摺動による摩擦の増大を避けることができる。また、作動流体の通過する流路の周囲に、摺動部分が生じないので、微小な異物の噛み込みによる摩擦の増大も生じない。 Also, in the first working fluid chamber, the distance between the end face of the opposite valve body and the port is a flow path through which the working fluid passes, so when adjusting the position of the end face of the valve body, the inside of the valve body and the first working fluid chamber It does not slide with the wall. Therefore, the increase in friction due to sliding can be avoided. In addition, since a sliding portion does not occur around the flow path through which the working fluid passes, the increase in friction due to the entrapment of minute foreign matter does not occur.
　第一作動流体室と第二作動流体室とが弁体の通路を介して連通しているので、第一作動流体室内の作動流体がポートを介して第一作動流体室外へ排出される流れの向きを基準として、弁体の下流側端と、前記下流側端の反対側端との圧力差が小さい。そのため、第一作動流体室と第二作動流体室との圧力差の発生を抑制できる。従って、図７に示すショックアブソーバのように付勢体の強化の必要性が生じない。ソレノイドの大型化を避けることができる。 Since the first working fluid chamber and the second working fluid chamber are in communication via the passage of the valve body, the flow of the working fluid in the first working fluid chamber is discharged to the outside of the first working fluid chamber through the port. The pressure difference between the downstream end of the valve body and the opposite end of the downstream end is small based on the direction. Therefore, generation of a pressure difference between the first working fluid chamber and the second working fluid chamber can be suppressed. Therefore, there is no need to strengthen the biasing body as in the shock absorber shown in FIG. The enlargement of the solenoid can be avoided.
　ソレノイドの非通電時には、付勢体により、弁体に対して、前記弁体の軸線方向に沿ってポートに向かう力が加えられる。このとき、弁体は、第一作動流体室内の作動流体を押し退けてポートに向けて移動するが、そのときの圧力が通路を介して第二作動流体室４０に伝播するため、第一作動流体室内の圧力の上昇が抑えられる。また、上述したように、弁体の移動時の摩擦の増大が防止されている。従って、付勢体の付勢力のみによって、迅速に弁体の端面とポートとの間隔を閉じることができる。このように、弁体がポートに向けて移動するときの弁体に対する抵抗（摩擦及び圧力上昇）の発生が極力抑えられているので、ソレノイドの非通電時における応答性に優れており、迅速にハード特性を得ることができる。 When the solenoid is not energized, the biasing body applies a force to the valve disc toward the port along the axial direction of the valve disc. At this time, the valve disc pushes away the working fluid in the first working fluid chamber and moves toward the port, but the pressure at that time propagates to the second working fluid chamber 40 through the passage, so the first working fluid The increase in pressure in the room can be suppressed. In addition, as described above, the increase in friction during movement of the valve body is prevented. Therefore, the gap between the end face of the valve body and the port can be quickly closed only by the biasing force of the biasing body. As described above, since the occurrence of resistance (friction and pressure increase) to the valve body as the valve body moves toward the port is suppressed as much as possible, the responsiveness at the time of non-energization of the solenoid is excellent, and the Hard characteristics can be obtained.
　従って、（１）のショックアブソーバは、通電不能となった場合にも良好な走行性能を確保しながら、小型であり、且つ制御可能な流量の範囲を広く確保できる。 Therefore, the shock absorber of (1) can ensure a wide range of compact and controllable flow rates while securing good running performance even when the current can not be supplied.
　（２）　（１）のショックアブソーバであって、
　前記通路は、前記弁体の軸線方向に沿って設けられており、前記ソレノイドが通電不能となり前記弁体と前記ポートとの間隔が狭くなるときに、前記第一作動流体室及び前記第二作動流体室のうち、高圧側の作動流体室から低圧側の作動流体室に作動流体を流すことにより、２つの作動流体室の間の圧力差を小さくすることが好ましい。 (2) The shock absorber of (1),
The passage is provided along the axial direction of the valve body, and the first working fluid chamber and the second operation are operated when the solenoid is not energized and the space between the valve body and the port becomes narrow. Among the fluid chambers, it is preferable to reduce the pressure difference between the two working fluid chambers by flowing the working fluid from the working fluid chamber on the high pressure side to the working fluid chamber on the low pressure side.
　（２）の構成によれば、第一作動流体室と第二作動流体室とを連通する通路が比較的短い。そのため、弁体の端面とポートとの間隔（作動流体の流路）を閉じるときに第一作動流体室と第二作動流体室との間の圧力伝達が速やかに生じる。これにより、第一作動流体室と第二作動流体室との圧力差の発生を、より効果的に抑制することができる。従って、更に応答性を高めることができる。 According to the configuration of (2), the passage communicating the first working fluid chamber and the second working fluid chamber is relatively short. Therefore, when the space between the end face of the valve body and the port (flow path of the working fluid) is closed, pressure transmission between the first working fluid chamber and the second working fluid chamber occurs rapidly. Thereby, the generation of the pressure difference between the first working fluid chamber and the second working fluid chamber can be suppressed more effectively. Therefore, responsiveness can be further enhanced.
　（３）　（２）のショックアブソーバであって、
　前記通路は、前記弁体の軸線方向に沿って前記弁体を貫通しており、前記ソレノイドが通電不能となり前記弁体と前記ポートとの間隔が狭くなるときに、前記第一作動流体室と前記第二作動流体室との圧力差を小さくするとともに、前記通路が前記ポートに近づく。。 (3) The shock absorber of (2),
The passage penetrates the valve body along the axial direction of the valve body, and when the solenoid is not energized and the distance between the valve body and the port becomes narrow, The pressure difference with the second working fluid chamber is reduced, and the passage approaches the port. .
　（３）の構成によれば、第一作動流体室と第二作動流体室とを連通する通路が更に短くなり、弁体とポートとの間隔が狭くなるときに通路がポートに近づくので、更に応答性を高めることができる。また、通路が弁体内に設けられるので、通路の形成スペースを弁体外に確保しなくてもよい。従って、弁の大型化を避けることができる。 According to the configuration of (3), the passage connecting the first working fluid chamber and the second working fluid chamber is further shortened, and the passage approaches the port when the distance between the valve body and the port narrows. Responsiveness can be improved. In addition, since the passage is provided in the valve body, the space for forming the passage may not be secured outside the valve. Therefore, enlargement of the valve can be avoided.
　（４）　（１）～（３）のいずれか１のショックアブソーバであって、
　前記付勢体は、前記第一作動流体室に設置され、前記弁体に対して、前記弁体の軸線方向に沿って前記ポートに向かう力を加えることが好ましい。 (4) The shock absorber according to any one of (1) to (3),
Preferably, the biasing body is installed in the first working fluid chamber and applies a force to the valve body in the axial direction of the valve body toward the port.
　（４）の構成によれば、前記付勢体により前記弁体を前記第一作動流体室側に引き出すことにより、前記弁体をスムーズに移動させることができるので、弁体の位置安定性及び応答性が更に向上する。 According to the configuration of (4), the valve body can be smoothly moved by pulling the valve body to the first working fluid chamber side by the biasing body, so that the positional stability of the valve body and Responsiveness is further improved.
　（５）　（１）～（４）のいずれか１のショックアブソーバであって、
　前記付勢体は、前記弁体の軸線方向において前記付勢体の一部が前記通路と重なる位置に設置され、前記弁体に対して、前記弁体の軸線方向に沿って前記ポートに向かう力を加えることが好ましい。 (5) The shock absorber according to any one of (1) to (4),
The biasing body is disposed at a position where a part of the biasing body overlaps the passage in the axial direction of the valve body, and the valve body is directed to the port along the axial direction of the valve body with respect to the valve body It is preferable to apply force.
　（５）の構成によれば、付勢体と弁体とをコンパクトに配置できるので、減衰力制御弁を小型化できる。 According to the configuration of (5), since the biasing body and the valve body can be disposed compactly, the damping force control valve can be miniaturized.
　（６）　（１）～（４）のいずれか１のショックアブソーバであって、
　前記付勢体は、前記弁体の軸線方向において前記付勢体の全部が前記通路と重なる位置に設置され、前記弁体に対して、前記弁体の軸線方向に沿って前記ポートに向かう力を加える。 (6) The shock absorber according to any one of (1) to (4),
The biasing body is disposed at a position where all of the biasing body overlaps the passage in the axial direction of the valve body, and a force directed to the port along the axial direction of the valve body with respect to the valve body Add
　（６）の構成によれば、付勢体と弁体とを更にコンパクトに配置できるので、減衰力制御弁を更に小型化できる。 According to the configuration of (6), since the biasing body and the valve body can be disposed more compactly, the damping force control valve can be further miniaturized.
　この発明の上述の目的およびその他の目的、特徴、局面および利点は、添付図面に関連して行われる以下のこの発明の実施形態の詳細な説明から一層明らかとなろう。 The above and other objects, features, aspects and advantages of the present invention will become more apparent from the following detailed description of embodiments of the present invention taken in conjunction with the accompanying drawings.
　本発明によれば、通電不能となった場合にも良好な走行性能を確保する構成としながら、小型であり、且つ制御可能な流量の範囲を広く確保できる。 According to the present invention, it is possible to secure a wide range of small-sized and controllable flow rates while securing good running performance even when the current can not be supplied.
本発明のショックアブソーバが備える減衰力制御弁の一例を模式的に示す縦断面図である。It is a longitudinal cross-sectional view which shows typically an example of the damping force control valve with which the shock absorber of this invention is equipped. 図１に示す減衰力制御弁の開状態（ａ）、微小開度状態（ｂ）、閉状態（ｃ）を模式的に示す縦断面図である。It is a longitudinal cross-sectional view which shows typically the open state (a) of the damping force control valve shown in FIG. 1, a micro opening degree state (b), and a closed state (c). 本発明に係る他の減衰力制御弁の開状態（ａ）、微小開度状態（ｂ）、閉状態（ｃ）を模式的に示す縦断面図である。It is a longitudinal cross-sectional view which shows typically the open state (a) of the other damping force control valve which concerns on this invention, a micro opening degree state (b), and a closed state (c). 本発明に係る他の減衰力制御弁の開状態（ａ）、微小開度状態（ｂ）、閉状態（ｃ）を模式的に示す縦断面図である。It is a longitudinal cross-sectional view which shows typically the open state (a) of the other damping force control valve which concerns on this invention, a micro opening degree state (b), and a closed state (c). 図１に示す減衰力制御弁を備えたショックアブソーバの一例を示す油圧回路図である。It is a hydraulic circuit figure which shows an example of the shock absorber provided with the damping force control valve shown in FIG. 図１に示す減衰力制御弁を備えたショックアブソーバの一例を示す油圧回路図である。It is a hydraulic circuit figure which shows an example of the shock absorber provided with the damping force control valve shown in FIG. 従来のショックアブソーバを模式的に示す縦断面図である。It is a longitudinal section showing a conventional shock absorber typically.
　以下、図面を参照してこの発明の実施の形態について説明する。
　先ず、本発明に係るショックアブソーバ１００が備える減衰力制御弁１０について説明する。
　図１は、本発明のショックアブソーバ１００が備える減衰力制御弁１０を模式的に示す縦断面図である。
　図１では、減衰力制御弁１０の非通電時における閉状態の様子を示している。
　以下の説明においては、第一作動流体室３０の作動流体が第一ポート３０ａを介して排出される方向を、下流方向Ｄと称する。また、弁体２０の軸線方向Ｓに沿って下流方向Ｄと反対の方向を、反対方向Ｕと称する。 Hereinafter, embodiments of the present invention will be described with reference to the drawings.
First, the damping force control valve 10 provided in the shock absorber 100 according to the present invention will be described.
FIG. 1 is a longitudinal sectional view schematically showing a damping force control valve 10 provided in a shock absorber 100 according to the present invention.
FIG. 1 shows the closed state of the damping force control valve 10 when it is not energized.
In the following description, the direction in which the working fluid of the first working fluid chamber 30 is discharged through the first port 30a is referred to as the downstream direction D. Further, a direction opposite to the downstream direction D along the axial direction S of the valve body 20 is referred to as an opposite direction U.
　減衰力制御弁１０は、中空筒状の外筒１１（ハウジング）を備える。外筒１１は、下流方向Ｄ側に開口１１ａを備え、反対方向Ｕ側に開口１１ｂを備える。外筒１１の開口１１ｂには、内筒１２が嵌め込まれている。外筒１１の反対方向U側端は、内側に曲げられ、軸線方向Ｓにおいて内筒１２と当接しており、これにより、外筒１１と内筒１２とが固定されている。外筒１１は、軸線方向Ｓにおける略中央部において軸心に向かって環状に突出するフランジ部１１ｃを有する。フランジ部１１ｃは、その内縁部において開口１１ｂに向かって延びる筒状部１１ｄを有する。筒状部１１ｄには、筒状のガイド部材１３が挿入される。ガイド部材１３は、下流方向Ｄ側にフランジ部１３ａを有する。フランジ部１１ｃ、１３ａは、互いに当接している。これにより、外筒１１内において、ガイド部材１３の反対方向Ｕ側への移動が規制される。ガイド部材１３は、ガイド孔１３ｂを備えている。ガイド孔１３ｂには、中空円筒状の弁体２０が摺動可能に挿入されている。 The damping force control valve 10 includes a hollow cylindrical outer cylinder 11 (housing). The outer cylinder 11 includes an opening 11 a on the downstream direction D side and an opening 11 b on the opposite direction U side. The inner cylinder 12 is fitted into the opening 11 b of the outer cylinder 11. The opposite direction U side end of the outer cylinder 11 is bent inward and abuts against the inner cylinder 12 in the axial direction S, whereby the outer cylinder 11 and the inner cylinder 12 are fixed. The outer cylinder 11 has a flange portion 11 c that annularly protrudes toward the axial center at a substantially central portion in the axial direction S. The flange portion 11c has a cylindrical portion 11d extending toward the opening 11b at its inner edge. The cylindrical guide member 13 is inserted into the cylindrical portion 11 d. The guide member 13 has a flange portion 13a on the downstream direction D side. The flanges 11c and 13a are in contact with each other. Thereby, in the outer cylinder 11, the movement to the opposite direction U side of the guide member 13 is regulated. The guide member 13 is provided with a guide hole 13b. A hollow cylindrical valve body 20 is slidably inserted into the guide hole 13b.
　弁体２０は、下流方向Ｄ側の端面２０ａと、反対方向Ｕ側の端面２０ｂとを有している。弁体２０は、端面２０ａから端面２０ｂまで延びる通路２１が形成されている。通路２１は、下流方向Ｄ側の端面２０ａを含む大径部２１ａと、大径部２１ａの反対方向Ｕ側端から第二作動流体室４０に向けて延びる連通部２１ｂとを含む。連通部２１ｂは、柱状空間であり、径は略一定である。弁体２０の下流方向Ｄ側の端面２０ａにおける通路２１（大径部２１ａ）の開口面積は、連通部２１ｂの開口面積よりも大きい。通路２１において、連通部２１ｂの径が最も小さい。即ち、減衰力制御弁１０において、連通部２１ｂが、通路２１内の最小径部である。軸線方向Ｓにおける大径部２１ａと連通部２１ｂとの境界は、第一作動流体室３０内に位置している。 The valve body 20 has an end face 20a on the downstream direction D side and an end face 20b on the opposite direction U side. The valve body 20 is formed with a passage 21 extending from the end face 20a to the end face 20b. The passage 21 includes a large diameter portion 21 a including an end surface 20 a on the downstream direction D side, and a communication portion 21 b extending toward the second working fluid chamber 40 from the opposite direction U side end of the large diameter portion 21 a. The communicating portion 21 b is a columnar space, and the diameter is substantially constant. The opening area of the passage 21 (large diameter part 21a) at the end face 20a on the downstream direction D side of the valve body 20 is larger than the opening area of the communication part 21b. In the passage 21, the diameter of the communication portion 21b is the smallest. That is, in the damping force control valve 10, the communication portion 21b is the smallest diameter portion in the passage 21. The boundary between the large diameter portion 21 a and the communication portion 21 b in the axial direction S is located in the first working fluid chamber 30.
　弁体２０の下流方向Ｄ側の端面２０ａは、第一作動流体室３０の第一ポート３０ａと対向する。端面２０ａは、第一作動流体室３０の壁面（底面２６ａ）と当接しない。弁体２０は、非磁性材料によって構成される。筒状部１１ｄの反対方向Ｕ側に、中空筒状の支持部材１４が設置されている。支持部材１４は、筒状部１１ｄと同軸上において筒状部１１ｄと対向する。支持部材１４は、下流方向Ｄ側に形成された開口１４ａと、反対方向Ｕ側に形成された開口１４ｂと、軸線方向Ｓにおける略中央部において軸心に向かって環状に突出するガイド部１４ｃとを有する。ガイド部１４ｃの内周側には、円環状の軸受２０ｃが設置されている。軸受２０ｃには、弁体２０が挿通されており、軸受２０ｃは、弁体２０を摺動可能に支持する。支持部材１４の内周面において、ガイド部１４ｃよりも開口１４ｂ側には、バネ受け部材１５が固定されている。バネ受け部材１５の外周面には、支持部材１４とバネ受け部材１５との間を密閉するための環状シール１６（例えば、Ｏリング）が設けられている。支持部材１４の反対方向Ｕ側端には、キャップ１７が設けられている。キャップ１７は、開口１４ｂを塞いでいる。支持部材１４内において、ガイド部１４ｃとバネ受け部材１５との間には、第二作動流体室４０が形成されている。 The end face 20 a on the downstream direction D side of the valve body 20 faces the first port 30 a of the first working fluid chamber 30. The end surface 20a does not abut on the wall surface (bottom surface 26a) of the first working fluid chamber 30. The valve body 20 is made of a nonmagnetic material. A hollow cylindrical support member 14 is installed on the opposite direction U side of the cylindrical portion 11 d. The support member 14 faces the cylindrical portion 11 d coaxially with the cylindrical portion 11 d. The supporting member 14 has an opening 14a formed on the downstream direction D side, an opening 14b formed on the opposite direction U side, and a guide portion 14c which annularly protrudes toward the axial center at a substantially central portion in the axial direction S Have. An annular bearing 20c is installed on the inner peripheral side of the guide portion 14c. The valve body 20 is inserted into the bearing 20c, and the bearing 20c slidably supports the valve body 20. A spring receiving member 15 is fixed on the inner peripheral surface of the support member 14 closer to the opening 14 b than the guide portion 14 c. An annular seal 16 (e.g., an O-ring) for sealing between the support member 14 and the spring receiving member 15 is provided on the outer peripheral surface of the spring receiving member 15. A cap 17 is provided at the opposite direction U side end of the support member 14. The cap 17 closes the opening 14 b. In the support member 14, a second working fluid chamber 40 is formed between the guide portion 14 c and the spring receiving member 15.
　第二作動流体室４０内に弁体２０の端面２０ｂが露出している。第二作動流体室４０内において、弁体２０の端面２０ｂと、バネ受け部材１５とによって、コイルバネ１８が支持される。コイルバネ１８は、弁体２０を下流方向Ｄに向けて付勢している。筒状部１１ｄと支持部材１４とを接続するように、筒状の筒部材１９が設けられている。筒部材１９は、非磁性材料によって構成される。外筒１１内には、ボビン２２が設けられている。ボビン２２は、支持部材１４の外周面、及び筒部材１９の外周面を覆う。ボビン２２には、ソレノイドコイル２３が巻かれている。外筒１１の内周面において、ボビン２２と、内筒１２との間には、円環板状のキャップ２４が取り付けられている。キャップ２４は、磁性材料（例えば鉄）によって構成される。 The end face 20 b of the valve body 20 is exposed in the second working fluid chamber 40. In the second working fluid chamber 40, the coil spring 18 is supported by the end face 20 b of the valve body 20 and the spring receiving member 15. The coil spring 18 biases the valve body 20 in the downstream direction D. A cylindrical cylindrical member 19 is provided to connect the cylindrical portion 11 d and the support member 14. The cylindrical member 19 is made of a nonmagnetic material. In the outer cylinder 11, a bobbin 22 is provided. The bobbin 22 covers the outer peripheral surface of the support member 14 and the outer peripheral surface of the cylindrical member 19. A solenoid coil 23 is wound around the bobbin 22. An annular plate-like cap 24 is attached between the bobbin 22 and the inner cylinder 12 on the inner peripheral surface of the outer cylinder 11. The cap 24 is made of a magnetic material (for example, iron).
　弁体２０の外周面において、ガイド部材１３と、ガイド部１４ｃとの間には、筒状のプランジャ２５が固定されている。筒状部１１ｄの内径は、プランジャ２５の外径よりも大きい。また、支持部材１４において、ガイド部１４ｃよりも開口１４ａ側の部分の内径は、プランジャ２５の外径よりも大きい。したがって、プランジャ２５は、ガイド部材１３とガイド部１４ｃとの間において軸線方向Ｓに移動できる。減衰力制御弁１０においては、ソレノイドコイル２３によって発生される磁界の磁束密度を調整することによって、プランジャ２５をガイド部材１３とガイド部１４ｃとの間で軸線方向Ｓに移動させることができる。それにより、弁体２０が軸線方向Ｓに移動する。ソレノイドコイル２３とコイルバネ１８とはソレノイドを構成する。プランジャ２５の設置空間２５ａは、筒状部１１ｄ、ガイド部材１３、ガイド部１４ｃおよび筒部材１９によって形成される。設置空間２５ａ内にも、作動流体ＨＯが充填されている。空間２５ａは、弁体２０の外周面とガイド部材１３の内周面との隙間を介して第一作動流体室３０に連通している。空間２５ａは、弁体２０の外周面とガイド部１４ｃの内周面との隙間を介して第二作動流体室４０に連通している。 On the outer peripheral surface of the valve body 20, a cylindrical plunger 25 is fixed between the guide member 13 and the guide portion 14c. The inner diameter of the cylindrical portion 11 d is larger than the outer diameter of the plunger 25. Further, in the support member 14, the inner diameter of the portion closer to the opening 14 a than the guide portion 14 c is larger than the outer diameter of the plunger 25. Therefore, the plunger 25 can move in the axial direction S between the guide member 13 and the guide portion 14c. In the damping force control valve 10, by adjusting the magnetic flux density of the magnetic field generated by the solenoid coil 23, the plunger 25 can be moved in the axial direction S between the guide member 13 and the guide portion 14c. Thereby, the valve body 20 moves in the axial direction S. The solenoid coil 23 and the coil spring 18 constitute a solenoid. The installation space 25 a of the plunger 25 is formed by the cylindrical portion 11 d, the guide member 13, the guide portion 14 c and the cylindrical member 19. The working fluid HO is also filled in the installation space 25a. The space 25 a communicates with the first working fluid chamber 30 via a gap between the outer peripheral surface of the valve body 20 and the inner peripheral surface of the guide member 13. The space 25 a communicates with the second working fluid chamber 40 through a gap between the outer peripheral surface of the valve body 20 and the inner peripheral surface of the guide portion 14 c.
　外筒１１内において開口１１ａ側には、ガイド部材１３のフランジ部１３ａに接触するように、有底の略円筒形状のバルブヘッド２６が設置されている。バルブヘッド２６の底面２６ａの中央には、第一ポート３０ａが形成されている。第一ポート３０ａは、弁体２０の端面２０ａと対向する位置に設置されている。バルブヘッド２６では、第一ポート３０ａから下流方向Ｄに向けて、作動流体路３１が延びている。バルブヘッド２６は、バルブヘッド２６の外周壁２６ｃに、第二ポート３０ｂを備えている。バルブヘッド２６では、第二ポート３０ｂから径方向に向けて、作動流体路３２が延びている。 A substantially cylindrical valve head 26 with a bottom is disposed on the side of the opening 11 a in the outer cylinder 11 so as to contact the flange portion 13 a of the guide member 13. A first port 30 a is formed at the center of the bottom surface 26 a of the valve head 26. The first port 30 a is installed at a position facing the end face 20 a of the valve body 20. In the valve head 26, the working fluid path 31 extends from the first port 30a in the downstream direction D. The valve head 26 is provided with a second port 30 b on the outer peripheral wall 26 c of the valve head 26. In the valve head 26, the working fluid passage 32 extends radially from the second port 30b.
　バルブヘッド２６とガイド部材１３とによって、第一作動流体室３０が構成されている。第一作動流体室３０は、ガイド孔１３ｂを備えている。第一作動流体室３０と第二作動流体室４０とは、弁体２０を挟んで対向配置されている。弁体２０の端面２０ａは、第一作動流体室３０側に配置されている。第一作動流体室３０と第二作動流体室４０とは、弁体２０の通路２１を介して連通している。弁体２０の外周面の周囲には、第一作動流体室３０内の空間が位置している。作動流体は、作動流体路３２から弁体２０の径方向に沿って第一作動流体室３０内に流入する。 A first working fluid chamber 30 is constituted by the valve head 26 and the guide member 13. The first working fluid chamber 30 is provided with a guide hole 13 b. The first working fluid chamber 30 and the second working fluid chamber 40 are disposed opposite to each other with the valve body 20 interposed therebetween. The end face 20 a of the valve body 20 is disposed on the first working fluid chamber 30 side. The first working fluid chamber 30 and the second working fluid chamber 40 are in communication via the passage 21 of the valve body 20. A space in the first working fluid chamber 30 is located around the outer peripheral surface of the valve body 20. The working fluid flows from the working fluid passage 32 along the radial direction of the valve body 20 into the first working fluid chamber 30.
　ショックアブソーバ１００では、ガイド孔１３ｂと第一ポート３０ａとが、第一作動流体室３０内の空間を挟んで、互いに対向する位置に形成されている。ガイド孔１３ｂと第一ポート３０ａとの距離は、第一ポート３０ａと第二ポート３０ｂとの距離よりも長い。ガイド孔１３ｂと第二ポート３０ｂとの距離は、第一ポート３０ａと第二ポート３０ｂとの距離よりも長い。軸線方向Ｓにおいて、第二ポート３０ｂは、ガイド孔１３ｂよりも第一ポート３０ａに近い。軸線方向Ｓにおいて、第二ポート３０ｂは、ガイド孔１３ｂと第一ポート３０ａとの間に設けられている。第一作動流体室３０内には、弁体２０と摺動する部材が設けられていない。
　ショックアブソーバ１００では、ガイド孔１３ｂと弁体２０とが摺動するが、ガイド孔１３ｂと弁体２０とが摺動する部分は、第一ポート３０ａ及び第二ポート３０ｂから離れた位置に設けられているので、微小な異物による摩擦の増加を抑制することができる。 In the shock absorber 100, the guide hole 13b and the first port 30a are formed at mutually opposing positions across the space in the first working fluid chamber 30. The distance between the guide hole 13b and the first port 30a is longer than the distance between the first port 30a and the second port 30b. The distance between the guide hole 13b and the second port 30b is longer than the distance between the first port 30a and the second port 30b. In the axial direction S, the second port 30b is closer to the first port 30a than the guide hole 13b. In the axial direction S, the second port 30 b is provided between the guide hole 13 b and the first port 30 a. In the first working fluid chamber 30, no member that slides on the valve body 20 is provided.
In the shock absorber 100, the guide hole 13b and the valve body 20 slide, but the portion where the guide hole 13b and the valve body 20 slide is provided at a position separated from the first port 30a and the second port 30b. Therefore, it is possible to suppress an increase in friction due to minute foreign matter.
　第一作動流体室３０内では、ガイド部材１３の下流側面１３ｃと、バルブヘッド２６の底面２６ａとが軸線方向Ｓに沿って対向している。第一作動流体室３０内において、弁体２０の外周には、固定具としてのサークリップ３３が固定されている。なお、固定具はサークリップに限定されない。 In the first working fluid chamber 30, the downstream side surface 13c of the guide member 13 and the bottom surface 26a of the valve head 26 are opposed in the axial direction S. In the first working fluid chamber 30, a circlip 33 as a fixture is fixed to the outer periphery of the valve body 20. In addition, a fixing tool is not limited to a circlip.
　サークリップ３３の下流方向Ｄ側において、サークリップ３３とバルブヘッド２６の底面２６ａとの間に、付勢体としてのコイルバネ３４が設置されている。コイルバネ３４には、弁体２０が挿通されている。下流方向Ｄに近づくにつれて、コイルバネ３４の径は大きくなっている。従って、作動流体路３２から第一作動流体室３０を介して作動流体路３１に至る作動流体の流れが、コイルバネ３４によって妨げられ難い。 Between the circlip 33 and the bottom surface 26 a of the valve head 26 on the downstream direction D side of the circlip 33, a coil spring 34 as a biasing body is installed. The valve body 20 is inserted into the coil spring 34. As the downstream direction D is approached, the diameter of the coil spring 34 increases. Therefore, the flow of the working fluid from the working fluid passage 32 to the working fluid passage 31 via the first working fluid chamber 30 is less likely to be blocked by the coil spring 34.
　固定具としてのサークリップ３３の反対方向Ｕ側において、サークリップ３３とガイド部材１３の下流側面１３ｃとの間に、付勢体としてのコイルバネ３５が設置されている。コイルバネ３５には、弁体２０が挿通されている。反対方向Ｕに近づくにつれて、コイルバネ３５の径が大きくなっている。 A coil spring 35 as an urging body is installed between the circlip 33 and the downstream side surface 13c of the guide member 13 on the opposite direction U side of the circlip 33 as a fixing tool. The valve body 20 is inserted through the coil spring 35. As the reverse direction U is approached, the diameter of the coil spring 35 increases.
　コイルバネ１８、３４、３５は、軸線方向Ｓに沿って、弁体２０に対して力を加える。減衰力制御弁１０では、ソレノイドコイル２３の非通電時に、コイルバネ１８、３４、３５によって、弁体２０が移動し、弁体２０が第一ポート３０ａを塞ぐ。なお、付勢体は、コイルバネに限定されず、例えば、板バネ等の従来公知の付勢体を採用できる。 The coil springs 18, 34, 35 apply a force to the valve body 20 along the axial direction S. In the damping force control valve 10, when the solenoid coil 23 is not energized, the valve body 20 is moved by the coil springs 18, 34, 35, and the valve body 20 closes the first port 30a. In addition, an urging body is not limited to a coil spring, For example, conventionally well-known urging bodies, such as a leaf | plate spring, are employable.
　次に、図２を用いて、減衰力制御弁１０の動作について説明する。
　図２は、図１に示す減衰力制御弁の開状態（ａ）、微小開度状態（ｂ）、閉状態（ｃ）の様子を模式的に示す縦断面図である。 Next, the operation of the damping force control valve 10 will be described with reference to FIG.
FIG. 2 is a longitudinal sectional view schematically showing the damping force control valve shown in FIG. 1 in an open state (a), a minute open state (b) and a closed state (c).
　減衰力制御弁１０では、弁体２０の端面２０ａ（図１参照）の一部（略半分）に、スラント加工が施されている。これにより、端面２０ａは、平坦部２０ｄと、平坦部２０ｄから反対方向Ｄに向けて傾斜する傾斜部２０ｅとからなる。ソレノイドコイル２３に通電され、減衰力制御弁１０が開状態であるときには、図２（ａ）に示すように、弁体２０が第一ポート３０ａから離れている。弁体２０と第一ポート３０ａとが離れているときには、弁体２０の全外周縁と第一ポート３０ａの全外周縁との間隔が、作動流体の流路Ｔである。 In the damping force control valve 10, a part (approximately half) of the end face 20a (see FIG. 1) of the valve body 20 is subjected to slant processing. Thus, the end face 20a includes the flat portion 20d and the inclined portion 20e which is inclined in the opposite direction D from the flat portion 20d. When the solenoid coil 23 is energized and the damping force control valve 10 is in the open state, as shown in FIG. 2A, the valve body 20 is separated from the first port 30a. When the valve body 20 and the first port 30a are separated, the distance between the entire outer peripheral edge of the valve body 20 and the entire outer peripheral edge of the first port 30a is the flow path T of the working fluid.
　図２（ａ）に示す状態において、ソレノイドコイル２３への通電が遮断されると、コイルバネ１８、３４、３５により、弁体２０が下流方向Ｄ側に移動する。このとき、通路２１も下流方向Ｄに向けて移動する。 In the state shown in FIG. 2A, when the solenoid coil 23 is deenergized, the valve body 20 is moved in the downstream direction D by the coil springs 18, 34, 35. At this time, the passage 21 also moves in the downstream direction D.
　図２（ｂ）は、弁体２０が下流方向Ｄ側に向けて移動しているときの様子を示しており、図２（ｂ）では、弁体２０の端面２０ａの平坦部２０ｄが、軸線方向Ｓにおいて、第一ポート３０ａと同位置に存在している。傾斜部２０ｅと第一ポート３０ａとの間には間隔が空いている。この間隔が、作動流体の流路Ｔである。弁体２０には大径部２１ａが形成されているので、作動流体の流路Ｔを通過した作動流体の一部が反対方向Ｕに流れるときに、大径部２１ａにおいて渦を成して拡散して下流方向Ｄに向かい易くなる。従って、第一作動流体室３０と第二作動流体室４０との圧力差の発生をより効率良く抑制できる。 FIG. 2B shows the valve body 20 moving in the downstream direction D. In FIG. 2B, the flat portion 20d of the end face 20a of the valve body 20 has an axis. In the direction S, it exists at the same position as the first port 30a. There is a space between the slope 20e and the first port 30a. This interval is the flow path T of the working fluid. Since the large diameter portion 21a is formed in the valve body 20, when part of the working fluid that has passed through the flow path T of the working fluid flows in the opposite direction U, it forms a vortex and diffuses in the large diameter portion 21a. It becomes easy to go to the downstream direction D. Therefore, the generation of the pressure difference between the first working fluid chamber 30 and the second working fluid chamber 40 can be suppressed more efficiently.
　また、図２（ｂ）に示すように、弁体２０の外周縁の一部が第一ポート３０ａ内に位置しているとき、流路Ｔは、弁体２０の外周縁の一部と第一ポート３０ａの外周縁の一部との間隔である。従って、弁体２０のストローク（軸線方向Ｓの変位量）に対する流路Ｔの開口面積の変化が比較的小さい。 Further, as shown in FIG. 2B, when a part of the outer peripheral edge of the valve body 20 is located in the first port 30a, the flow path T is a part of the outer peripheral edge of the valve body 20 and the first It is a distance from a part of the outer peripheral edge of one port 30a. Therefore, the change in the opening area of the flow passage T with respect to the stroke (displacement amount in the axial direction S) of the valve body 20 is relatively small.
　弁体２０は、コイルバネ１８、３４、３５により、図２（ｂ）に示す状態から、更に下流方向Ｄに移動し、図２（ｃ）に示す位置で停止する。この位置が、弁体２０の閉位置である。閉位置は、ソレノイドコイル２３の非通電時にコイルバネ１８、３４、３５により弁体２０が移動する最も下流方向Ｄ側の位置である。弁体２０が閉位置にあるとき、第一ポート３０ａは、弁体２０によって閉じられていることが好ましい。言い換えると、弁体２０が閉位置にあるとき、第一ポート３０ａが、弁体２０によって実質的に全閉状態となっていることが好ましい。ここでいう実質的に全閉状態とは、使用状態等によって若干量の開きが生じる場合が許容されることを意味している。第一ポート３０ａは、弁体２０によって完全に全閉状態となってもよい。ショックアブソーバ１００では、弁体２０が閉位置に位置するとき、通路２１の下流方向Ｄ側端が第一ポート３０ａ内に入り、通路２１が作動流体室３１と連通する。 The valve body 20 is further moved in the downstream direction D from the state shown in FIG. 2B by the coil springs 18, 34, 35, and stops at the position shown in FIG. 2C. This position is the closed position of the valve body 20. The closed position is the position on the most downstream direction D side where the valve body 20 is moved by the coil springs 18, 34, 35 when the solenoid coil 23 is not energized. When the valve body 20 is in the closed position, the first port 30 a is preferably closed by the valve body 20. In other words, it is preferable that the first port 30 a be substantially fully closed by the valve body 20 when the valve body 20 is in the closed position. The term "substantially fully closed state" as used herein means that a case where a slight amount of opening occurs depending on the use state or the like is allowed. The first port 30 a may be completely closed by the valve body 20. In the shock absorber 100, when the valve body 20 is in the closed position, the downstream direction D side end of the passage 21 enters the first port 30a, and the passage 21 communicates with the working fluid chamber 31.
　弁体２０には、第一作動流体室３０と第二作動流体室４０とを連通する通路２１が形成されているので、図２（ａ）～図２（ｃ）に示すように、減衰力制御弁１０が開状態から閉状態に移行するとき、第一作動流体室３０内の作動流体の圧力が第二作動流体室４０に伝わるので、第一作動流体室３０と第二作動流体室４０との圧力差の発生を抑制することができる。従って、ソレノイドの非通電時にコイルバネ１８、３４、３５によって弁体２０を迅速に閉位置まで移動させることができる。 Since the passage 21 which connects the first working fluid chamber 30 and the second working fluid chamber 40 is formed in the valve body 20, as shown in FIGS. 2 (a) to 2 (c), the damping force is reduced. When the control valve 10 shifts from the open state to the closed state, the pressure of the working fluid in the first working fluid chamber 30 is transmitted to the second working fluid chamber 40, so the first working fluid chamber 30 and the second working fluid chamber 40. Generation of a pressure difference with the Therefore, when the solenoid is not energized, the valve body 20 can be quickly moved to the closed position by the coil springs 18, 34, 35.
　次に、減衰力制御弁の他の実施形態について説明する。
　図３は、本発明における他の実施形態に係る減衰力制御弁の開状態（ａ）、微小開度状態（ｂ）、閉状態（ｃ）を模式的に示す縦断面図である。図３は、弁体２０の下流方向Ｄ側端の形状を除いて、図２と同じであるから、図３においては、図２と同一の構成に対して同一の符号を付し、その説明を省略又は簡略化する。 Next, another embodiment of the damping force control valve will be described.
FIG. 3 is a longitudinal sectional view schematically showing an open state (a), a minute open state (b) and a closed state (c) of a damping force control valve according to another embodiment of the present invention. 3 is the same as FIG. 2 except for the shape of the downstream end D side end of the valve body 20, in FIG. 3, the same reference numerals are given to the same configuration as FIG. Omit or simplify.
　図３に示す減衰力制御弁１０では、弁体２０の下流方向Ｄ側の端面２０ａ´が平坦である。図３（ａ）に示す状態においてソレノイドコイル２３が非通電状態となると、弁体２０が下流方向Ｄに移動する。これにより、減衰力制御弁１０が微小開度になる。このとき、図３（ｂ）に示すように、流路Ｔは、弁体２０の全外周縁と第一ポート３０ａの全開周縁との間隔である。その後、弁体２０は、更に下流方向Ｄに移動し、図３（ｃ）に示すように、弁体２０の端面２０ａ´と第一ポート３０ａとが軸線方向Ｓにおいて同位置に存在し、弁体２０の端面２０ａ´によって第一ポート３０ａが閉じられる。このとき、弁体２０の端面２０ａ´は、閉位置に位置している。 In the damping force control valve 10 shown in FIG. 3, the end face 20 a ′ on the downstream direction D side of the valve body 20 is flat. When the solenoid coil 23 is deenergized in the state shown in FIG. 3A, the valve body 20 moves in the downstream direction D. Thereby, the damping force control valve 10 becomes a minute opening degree. At this time, as shown in FIG. 3B, the flow path T is the distance between the entire outer peripheral edge of the valve body 20 and the fully open peripheral edge of the first port 30a. Thereafter, the valve body 20 is further moved in the downstream direction D, and as shown in FIG. 3C, the end face 20a 'of the valve body 20 and the first port 30a exist at the same position in the axial direction S. The end face 20a 'of the body 20 closes the first port 30a. At this time, the end face 20a 'of the valve body 20 is located at the closed position.
　次に、本発明の他の実施形態について説明する。
　図４は、本発明の他の実施形態に係る減衰力制御弁の開状態（ａ）、微小開度状態（ｂ）、閉状態（ｃ）を模式的に示す縦断面図である。なお、図４は、弁体２０の下流方向Ｄ側端の形状を除いて、図２と同じであるから、図４においては、図２と同一の構成に対してっ同一の符号を付し、その説明を省略又は簡略化する。 Next, another embodiment of the present invention will be described.
FIG. 4 is a longitudinal sectional view schematically showing an open state (a), a minute opening degree state (b) and a closed state (c) of a damping force control valve according to another embodiment of the present invention. 4 is the same as FIG. 2 except for the shape of the downstream direction D side end of the valve body 20, in FIG. 4 the same reference numerals are given to the same configuration as FIG. , Omit or simplify the explanation.
　図４に示す減衰力制御弁１０では、弁体２０は、軸線方向Ｓに弁体２０を貫通する通路２１を備えているが、大径部２１ａは形成されていない。弁体２０は、円環形状の端面２０ａ´´を備えている。図４（ａ）に示す状態においてソレノイドコイル２３が非通電状態となると、弁体２０が下流方向Ｄに移動する。これにより、減衰力制御弁１０が微小開度になる。このとき、図４（ｂ）に示すように、流路Ｔは、弁体２０の全外周縁と第一ポート３０ａの全開周縁との間隔である。その後、弁体２０は、更に下流方向Ｄに移動し、図４（ｃ）に示すように、弁体２０の端面２０ａ´´と第一ポート３０ａとが軸線方向Ｓにおいて同位置に存在し、弁体２０の端面２０ａ´によって第一ポート３０ａが閉じられる。このとき、弁体２０の端面２０ａ´は、閉位置に位置している。 In the damping force control valve 10 shown in FIG. 4, the valve body 20 includes the passage 21 penetrating the valve body 20 in the axial direction S, but the large diameter portion 21 a is not formed. The valve body 20 is provided with an annular end surface 20 a ′ ′. When the solenoid coil 23 is deenergized in the state shown in FIG. 4A, the valve body 20 moves in the downstream direction D. Thereby, the damping force control valve 10 becomes a minute opening degree. At this time, as shown in FIG. 4B, the flow path T is the distance between the entire outer peripheral edge of the valve body 20 and the fully open peripheral edge of the first port 30a. Thereafter, the valve body 20 is further moved in the downstream direction D, and as shown in FIG. 4C, the end face 20a '' of the valve body 20 and the first port 30a exist at the same position in the axial direction S, The end face 20a 'of the valve body 20 closes the first port 30a. At this time, the end face 20a 'of the valve body 20 is located at the closed position.
　図３及び図４に示す減衰力制御弁１０においても、通路２１によって、第一作動流体室３０と第二作動流体室４０との作動流体の圧力差の発生を抑制できるので、弁体２０を速やかに閉位置に移動させることができる。 Also in the damping force control valve 10 shown in FIG. 3 and FIG. 4, since the passage 21 can suppress the generation of the pressure difference between the working fluid of the first working fluid chamber 30 and the second working fluid chamber 40 It can be quickly moved to the closed position.
　次に、本発明の一実施形態に係るショックアブソーバ１００について説明する。
　図５及び図６は、図１に示す減衰力制御弁１０を備えたショックアブソーバ１００を示す油圧回路図である。 Next, a shock absorber 100 according to an embodiment of the present invention will be described.
5 and 6 are hydraulic circuit diagrams showing a shock absorber 100 provided with the damping force control valve 10 shown in FIG.
　ショックアブソーバ１００は、油圧シリンダ１１２を備える。油圧シリンダ１１２内には、ピストンアセンブリ１４４が設置されている。油圧シリンダ１１２内は、ピストンアセンブリ１４４によって、２つの作動流体室１５８、１６０に区画されている。ピストンロッド１６２の一端は、油圧シリンダ１１２の一端側から、油圧シリンダ１１２内に挿入されており、ピストンアセンブリ１４４に固定されている。ピストンロッド１６２の他端は、車両の車体側（図示せず）に接続されている。また、油圧シリンダ１１２の他端は、車体の車輪側（図示せず）に接続されている。 The shock absorber 100 is provided with a hydraulic cylinder 112. In the hydraulic cylinder 112, a piston assembly 144 is installed. The hydraulic cylinder 112 is divided into two working fluid chambers 158 and 160 by a piston assembly 144. One end of the piston rod 162 is inserted into the hydraulic cylinder 112 from one end side of the hydraulic cylinder 112 and is fixed to the piston assembly 144. The other end of the piston rod 162 is connected to the vehicle body side (not shown) of the vehicle. The other end of the hydraulic cylinder 112 is connected to the wheel side (not shown) of the vehicle body.
　減衰力発生部としてのピストンアセンブリ１４４は、複数枚のシムを備えた減衰バルブ１４８、１５０を備えている。減衰バルブ１４８は、作動流体室１６０から作動流体室１５８へ作動流体を流すことができ、このときに減衰力が発生する（伸び減衰）。その逆方向には作動流体を流すことはできない。減衰バルブ１５０は、作動流体室１５８から作動流体室１６０へ作動流体を流すことができ、このときに減衰力が発生する（縮み減衰）。その逆方向に作動流体を流すことはできない。 The piston assembly 144 as a damping force generator includes damping valves 148 and 150 with a plurality of shims. The damping valve 148 can flow the working fluid from the working fluid chamber 160 to the working fluid chamber 158, at which time a damping force is generated (elongation damping). The working fluid can not flow in the opposite direction. The damping valve 150 can flow the working fluid from the working fluid chamber 158 to the working fluid chamber 160, at which time a damping force is generated (shrinkage damping). The working fluid can not flow in the opposite direction.
　作動流体室１５８と、リザーバタンク１１４との間には、減衰力調整装置１１６が設置されている。減衰力調整装置１１６では、減衰力制御弁１０と、複数枚のシムを備えた減衰バルブ１１６ｂと、チェックバルブ１１６ｃとが並列に設置されている。減衰バルブ１１６ｂは、油圧シリンダ１１２側からリザーバタンク１１４側に作動流体を流すことができ、その逆方向には作動流体を流すことができない。チェックバルブ１１６ｃは、リザーバタンク１１４側から油圧シリンダ１１２側に作動流体を流すことができる。その逆方向には作動流体を流すことができない。リザーバタンク１１４内には、作動流体Ｏと気体Ｇとが収容されており、作動流体Ｏと気体Ｇとが界面ＯＳで接触している。作動流体Ｏは、例えば、作動油等である。気体Ｇは、例えば、窒素ガスや空気等である。 A damping force adjustment device 116 is installed between the working fluid chamber 158 and the reservoir tank 114. In the damping force adjustment device 116, the damping force control valve 10, a damping valve 116b having a plurality of shims, and a check valve 116c are installed in parallel. The damping valve 116 b can flow the working fluid from the hydraulic cylinder 112 side to the reservoir tank 114 side, and can not flow the working fluid in the opposite direction. The check valve 116 c can flow the working fluid from the reservoir tank 114 side to the hydraulic cylinder 112 side. The working fluid can not flow in the opposite direction. The working fluid O and the gas G are contained in the reservoir tank 114, and the working fluid O and the gas G are in contact at the interface OS. The working fluid O is, for example, working oil or the like. The gas G is, for example, nitrogen gas or air.
　減衰力制御弁１０は、図２（ａ）、（ｂ）、図３（ａ）、（ｂ）、及び図４（ａ）、（ｂ）に示す状態においては、作動流体を、作動流体路３２から第一作動流体室３０を介して作動流体路３１に向かう方向に流すことができる。また、減衰力制御弁１０は、その逆方向に流すことも可能である。また、減衰力制御弁１０は、図５及び図６に示すように、減衰バルブ１１６ｂに対するバイパスとして設置されている。 The damping force control valve 10, in the state shown in FIGS. 2 (a) and 2 (b), 3 (a) and 3 (b), and FIGS. 4 (a) and 4 (b), the working fluid It is possible to flow from 32 to the working fluid passage 31 via the first working fluid chamber 30. The damping force control valve 10 can also flow in the opposite direction. Further, as shown in FIGS. 5 and 6, the damping force control valve 10 is installed as a bypass for the damping valve 116b.
　ピストンアセンブリ１４４がＸ１方向に移動するとき、油圧シリンダ１１２内に入ったピストンロッド１６２の体積分の作動流体が、油圧シリンダ１１２から排出され、リザーバタンク１１４に移動する。減衰力制御弁１０と減衰バルブ１１６ｂとは互いにバイパスの関係にあり、油圧シリンダ１１２から排出された作動流体ＨＯは、図５に示すように、減衰力制御弁１０および減衰バルブ１１６ｂを通過してリザーバタンク１１４に流入する。減衰力制御弁１０では、作動流体が第一作動流体室３０から第一ポート３０ａを介して排出される向きに流れる。減衰力調整装置１１６（減衰バルブ１１６ｂ及び減衰力制御弁１０）を流れる時の抵抗が、油圧シリンダ１１２内の作動流体の圧力を増大させ、ピストンロッド１６２のＸ１方向の移動に抵抗する力（シリンダ内の作動流体の圧力×ピストンロッド１６２の断面積）、即ち圧縮減衰力（１）が発生する。ここで減衰力制御弁１０の開度を調整すると、減衰バルブ１１６ｂと減衰力制御弁１０との流量の割合が変化するので、減衰バルブ１１６の抵抗が調整されて、ピストンロッド１６２に作用する圧縮減衰力が調整される。また、ピストンアセンブリ１４４の減衰バルブ１５０にも作動流体室１５８から作動流体室１６０の方向に作動流体が流れ、そのときの抵抗がピストンアセンブリ１４４に作用し、ピストンロッド１６２に圧縮減衰力（２）として付加される。 When the piston assembly 144 moves in the X1 direction, the working fluid of the volume of the piston rod 162 that has entered the hydraulic cylinder 112 is discharged from the hydraulic cylinder 112 and moves to the reservoir tank 114. Damping force control valve 10 and damping valve 116b are in a bypass relationship with each other, and the working fluid HO discharged from hydraulic cylinder 112 passes damping force control valve 10 and damping valve 116b as shown in FIG. It flows into the reservoir tank 114. In the damping force control valve 10, the working fluid flows in the direction of being discharged from the first working fluid chamber 30 via the first port 30a. The resistance when flowing through the damping force adjusting device 116 (the damping valve 116b and the damping force control valve 10) increases the pressure of the working fluid in the hydraulic cylinder 112 and resists the movement of the piston rod 162 in the X1 direction (cylinder The pressure of the working fluid (cross sectional area of the piston rod 162), that is, the compression damping force (1) is generated. Here, when the opening degree of the damping force control valve 10 is adjusted, the ratio of the flow rate between the damping valve 116 b and the damping force control valve 10 changes, so that the resistance of the damping valve 116 is adjusted and the compression acting on the piston rod 162 Damping force is adjusted. Also, the working fluid flows from the working fluid chamber 158 toward the working fluid chamber 160 also in the damping valve 150 of the piston assembly 144, and the resistance at that time acts on the piston assembly 144 and the compression damping force (2) on the piston rod 162 Is added as
　一方、ピストンアセンブリ１４４がＸ２方向に移動するとき、図６に示すように、ピストンロッド１６２が退出した体積分の作動流体が、チェックバルブ１１６ｃを抵抗なく通過して油圧シリンダ１１２に戻る。
　このように、ショックアブソーバ１００では、圧縮時の減衰力の一部を減衰力制御弁１０により調整可能である。具体的には、ショックアブソーバ１００では、圧縮時の減衰力（即ち、上記の圧縮減衰力（１）及び（２））のうち、ピストンロッド１６２の進入により発生する圧縮減衰力（１）を調整することができる。
　なお、本発明は、この例に限定されず、ショックアブソーバ１００は、例えば、圧縮時の減衰力の全部を減衰力制御弁１０により調整可能であってもよい。具体的には、図６及び図７に示す例において、減衰バルブ１５０に代えて、作動流体室１５８から作動流体室１６０に作動流体を流すチェックバルブが設けられていてもよい。このように構成されたショックアブソーバ１００では、ピストンアセンブリ１４４がＸ１方向に移動するとき、上記の圧縮減衰力（１）が生じるが、上記の圧縮減衰力（２）が生じない。従って、圧縮減衰力（１）を調整することにより、圧縮時の減衰力の全部を調整することができる。 On the other hand, when the piston assembly 144 moves in the X2 direction, as shown in FIG. 6, the working fluid of the volume from which the piston rod 162 is withdrawn passes through the check valve 116 c without resistance and returns to the hydraulic cylinder 112.
Thus, in the shock absorber 100, part of the damping force at the time of compression can be adjusted by the damping force control valve 10. Specifically, in the shock absorber 100, the compression damping force (1) generated by the approach of the piston rod 162 in the damping forces during compression (ie, the above-mentioned compression damping forces (1) and (2)) is adjusted can do.
The present invention is not limited to this example, and for example, the shock absorber 100 may be capable of adjusting all of the damping force at the time of compression by the damping force control valve 10. Specifically, in the example shown in FIG. 6 and FIG. 7, instead of the damping valve 150, a check valve may be provided to flow the working fluid from the working fluid chamber 158 to the working fluid chamber 160. In the shock absorber 100 configured as described above, when the piston assembly 144 moves in the X1 direction, the above-described compression damping force (1) is generated, but the above-described compression damping force (2) is not generated. Therefore, by adjusting the compression damping force (1), it is possible to adjust all of the damping forces at the time of compression.
　以上、ショックアブソーバ１００によれば、弁体２０の端面２０ａと第一ポート３０ａとが対向しており、弁体２０の端面２０ａの全外周縁と第一ポート３０ａの全外周縁との間隙が、作動流体の流路Ｔである。流路Ｔの開度は、弁体２０の端面２０ａの位置によって変更され、これにより減衰力が制御される。弁体２０のストロークに対する流路面積の変化量が大きいので、弁体２０の径を大きくすることなく、減衰力発生部としての減衰バルブ１１６ｂに対するバイパスにおいて制御可能な流量の範囲を広く確保できる。 As described above, according to the shock absorber 100, the end face 20a of the valve body 20 and the first port 30a face each other, and the gap between the entire outer peripheral edge of the end face 20a of the valve body 20 and the entire outer peripheral edge of the first port 30a is , Flow path T of the working fluid. The opening degree of the flow path T is changed by the position of the end face 20a of the valve body 20, whereby the damping force is controlled. Since the amount of change in the flow passage area with respect to the stroke of the valve body 20 is large, a wide controllable flow rate range can be secured in the bypass with respect to the damping valve 116b as the damping force generating portion without increasing the diameter of the valve body 20.
　また、第一作動流体室３０において、弁体２０の端面２０ａと第一ポート３０ａとの間隔が、作動流体の流路Ｔなので、弁体２０の端面２０ａの位置調整時に、弁体２０と第一作動流体室３０の内壁面とが摺動しない。従って、摺動による摩擦の増大を避けることができる。また、作動流体の流路Ｔの周囲に、摺動部分が生じないので、微小な異物の噛み込みによる摩擦の増大も生じない。 In the first working fluid chamber 30, the distance between the end face 20a of the valve body 20 and the first port 30a is the flow path T of the working fluid, so when adjusting the position of the end face 20a of the valve body 20, The inner wall surface of the working fluid chamber 30 does not slide. Therefore, the increase in friction due to sliding can be avoided. In addition, since a sliding portion does not occur around the flow path T of the working fluid, an increase in friction due to entrapment of minute foreign matter does not occur.
　また、第一作動流体室３０と第二作動流体室４０とが弁体２０の通路２１を介して連通しているので、弁体２０の下流方向Ｄ側の端面２０ａと、反対方向Ｕ側の端面２０ｂとの圧力差が小さい。そのため、第一作動流体室３０と第二作動流体室４０との圧力差の発生を抑制できる。その結果、ソレノイドの大型化を避けることができる。 Further, since the first working fluid chamber 30 and the second working fluid chamber 40 communicate with each other through the passage 21 of the valve body 20, the end face 20a on the downstream direction D side of the valve body 20 and the opposite direction U side The pressure difference with the end face 20b is small. Therefore, the generation of the pressure difference between the first working fluid chamber 30 and the second working fluid chamber 40 can be suppressed. As a result, enlargement of the solenoid can be avoided.
　ソレノイドの非通電時には、コイルバネ１８、３４、３５により、弁体２０に対して、弁体２０の軸線方向に沿って第一ポート３０ａに向かう力が加えられる。このとき、弁体２０は、第一作動流体室３０内の作動流体を押し退けて第一ポート３０ａに向けて移動するが、そのときの圧力が通路２１を介して第二作動流体室４０に伝播するため、第一作動流体室３０の圧力の上昇が抑えられる。また、第一作動流体室３０内では弁体２０と他部材との摺動が発生しないので、弁体２０の移動時の摩擦の増大が防止されている。従って、コイルバネ１８、３４、３５の付勢力のみによって、迅速に弁体２０の端面２０ａと第一ポート３０ａとの間隔を閉じることができる。このように、弁体２０が第一ポート３０ａに向けて移動するときの弁体２０に対する抵抗（摩擦及び圧力上昇）の発生が極力抑えられているので、ソレノイドの非通電時における応答性に優れており、迅速にハード特性を得ることができる。従って、ショックアブソーバ１００は、通電不能となった場合にも良好な走行性能を確保しながら、小型であり、且つ制御可能な流量の範囲を広く確保できる。 When the solenoid is not energized, the coil springs 18, 34, 35 apply a force to the valve body 20 toward the first port 30a along the axial direction of the valve body 20. At this time, the valve body 20 displaces the working fluid in the first working fluid chamber 30 and moves toward the first port 30 a, but the pressure at that time propagates to the second working fluid chamber 40 via the passage 21. As a result, the pressure increase of the first working fluid chamber 30 is suppressed. Further, since the sliding movement between the valve body 20 and the other members does not occur in the first working fluid chamber 30, an increase in friction during movement of the valve body 20 is prevented. Therefore, the gap between the end face 20a of the valve body 20 and the first port 30a can be quickly closed only by the biasing force of the coil springs 18, 34, 35. As described above, since the occurrence of resistance (friction and pressure increase) to the valve body 20 when the valve body 20 moves toward the first port 30a is suppressed as much as possible, the responsiveness at the time of non-energization of the solenoid is excellent. Can quickly obtain hard characteristics. Therefore, the shock absorber 100 can ensure a wide range of small and controllable flow rates while securing good traveling performance even when the current can not be supplied.
　また、通路２１が弁体２０の軸線方向に沿って弁体２０を貫通しているので、通路２１が短い。従って、ソレノイドコイル２３が通電不能となり弁体２０と第一ポート３０ａとの間隔が狭くなるときに、高圧側の第一作動流体室３０と低圧側の第二作動流体室４０との圧力差を速やかに小さくすることができ、応答性に優れる。また、通路２１が弁体２０内に設けられるので、通路２１の形成スペースを弁体２０外に確保しなくてもよい。従って、弁の大型化を避けることができる。 In addition, since the passage 21 penetrates the valve body 20 along the axial direction of the valve body 20, the passage 21 is short. Therefore, when the solenoid coil 23 can not be energized and the distance between the valve body 20 and the first port 30a becomes narrow, the pressure difference between the first working fluid chamber 30 on the high pressure side and the second working fluid chamber 40 on the low pressure side It can be made smaller quickly and has excellent responsiveness. Further, since the passage 21 is provided in the valve body 20, the space for forming the passage 21 may not be secured outside the valve body 20. Therefore, enlargement of the valve can be avoided.
　また、コイルバネ３４、３５が、第一作動流体室３０に設置され、弁体２０に対して、弁体２０の軸線方向に沿って第一ポート３０ａに向かう力を加えるため、弁体２０を第一作動流体室３０側にスムーズに引き出すことができる。 Further, the coil spring 34, 35 is disposed in the first working fluid chamber 30, and in order to apply a force toward the first port 30a along the axial direction of the valve body 20 to the valve body 20, One working fluid chamber 30 can be smoothly pulled out.
　さらに、コイル３４、３５は、弁体２０の軸線方向Ｓにおいてコイル３４、３５が通路２１と重なる位置に設置され、弁体２０に対して、弁体２０の軸線方向Ｓに沿って第一ポート３０ａに向かう力を加える。従って、コイルバネ３４、３５と弁体２０とを更にコンパクトに配置できるので、減衰力制御弁１０を更に小型化できる。 Furthermore, the coils 34 and 35 are disposed at positions where the coils 34 and 35 overlap the passage 21 in the axial direction S of the valve body 20, and the first port along the axial direction S of the valve body 20 with respect to the valve body 20. Add force towards 30a. Therefore, since the coil springs 34 and 35 and the valve body 20 can be disposed more compactly, the damping force control valve 10 can be further miniaturized.
　上述の実施形態では、減衰力制御弁１０を油圧シリンダ１１２に接続する場合について説明したが、減衰力調整装置の配置方法は上述の例に限定されない。図５及び図６に示すショックアブソーバ１００は、減衰力制御弁１０に対して作動流体を両方向に流すことができるように構成されていたが、本発明は、この例に限定されない。本発明では、少なくとも第一作動流体室３０から第一ポート３０ａを介して作動流体を排出する方向に作動流体を流すことができるように構成されていることが好ましい。また、ショックアブソーバ１００は、伸長時に第一作動流体室３０から第一ポート３０ａを介して作動流体を排出する方向に作動流体を流すように構成されていてもよく、縮退時に第一作動流体室３０から第一ポート３０ａを介して作動流体を排出する方向に作動流体を流すように構成されていてもよい。 Although the above-mentioned embodiment explained the case where damping force control valve 10 was connected to hydraulic cylinder 112, the arrangement method of a damping force adjustment device is not limited to the above-mentioned example. Although the shock absorber 100 shown in FIGS. 5 and 6 is configured to allow the working fluid to flow in both directions with respect to the damping force control valve 10, the present invention is not limited to this example. In the present invention, preferably, the working fluid can be made to flow in a direction in which the working fluid is discharged from at least the first working fluid chamber 30 via the first port 30a. In addition, the shock absorber 100 may be configured to flow the working fluid in a direction to discharge the working fluid from the first working fluid chamber 30 via the first port 30a at the time of extension, and at the time of retraction, the first working fluid chamber 30 may be configured to flow the working fluid in the direction of discharging the working fluid via the first port 30a.
　ショックアブソーバ１００では、油圧シリンダ１１２とリザーバタンク１１４との間に、減衰力調整装置１１６が設置され、減衰力調整装置１１６内に、縮み減衰力を発生させる減衰力発生部としてのチェックバルブ１１６ｃが設置されており、減衰バルブ１１６ｂに対するバイパス内に減衰力制御弁１０が設置されている。縮退時に、減衰力調整装置１１６では、油圧シリンダ１１２内に進入するピストンロッド１６２の体積分の作動流体が流れる。この作動流体の一部は、減衰バルブ１１６ｂを流れ、作動流体の残部は、減衰力制御弁１０を流れる。このとき、減衰バルブ１１６ｂと減衰力制御弁１０とは互いにバイパスの関係にある。なお、本発明は、この例に限定されない。例えば、ショックアブソーバ１００において、チェックバルブ１１６ｃに代えて、減衰力発生部としての減衰バルブが設置されていてもよい。この場合、減衰力制御弁１０は、伸び減衰力を発生させるチェックバルブ１１６ｃに対するバイパス内に設置されていることになる。伸長時に、減衰力調整装置１１６では、油圧シリンダ１１２内から退出するピストンロッド１６２の体積分の作動流体が流れる。この作動流体の一部は、減衰バルブを流れ、作動流体の残部は、減衰力制御弁１０を流れる。このとき、減衰バルブと減衰力制御弁１０とは互いにバイパスの関係にある。 In the shock absorber 100, a damping force adjustment device 116 is installed between the hydraulic cylinder 112 and the reservoir tank 114, and a check valve 116c as a damping force generation unit for generating a contraction damping force is provided in the damping force adjustment device 116. The damping force control valve 10 is installed in the bypass for the damping valve 116b. At the time of retraction, in the damping force adjustment device 116, the working fluid of the volume of the piston rod 162 entering the hydraulic cylinder 112 flows. A portion of the working fluid flows through the damping valve 116 b, and the remaining portion of the working fluid flows through the damping force control valve 10. At this time, the damping valve 116 b and the damping force control valve 10 are in a bypass relationship with each other. The present invention is not limited to this example. For example, in the shock absorber 100, instead of the check valve 116c, a damping valve as a damping force generation unit may be installed. In this case, the damping force control valve 10 is installed in the bypass to the check valve 116c that generates the stretching damping force. At the time of extension, in the damping force adjustment device 116, the working fluid flows by the volume of the piston rod 162 which is withdrawn from the inside of the hydraulic cylinder 112. A portion of the working fluid flows through the damping valve, and the remaining portion of the working fluid flows through the damping force control valve 10. At this time, the damping valve and the damping force control valve 10 are in a bypass relationship with each other.
　このように、本発明では、減衰力制御弁１０が、油圧シリンダ１１２外において、縮み減衰力を発生させる減衰力発生部（減衰バルブ１１６ｂ）に対するバイパス中に設置されてもよく、伸び減衰力を発生させる減衰力発生部に対するバイパス中に設置されてもよく、両方のバイパス中に設置されてもよい。 As described above, in the present invention, the damping force control valve 10 may be installed outside the hydraulic cylinder 112 in a bypass for the damping force generating portion (the damping valve 116b) that generates the contraction damping force. It may be installed in the bypass for the damping force generating part to generate, and may be installed in both bypasses.
　また、減衰力制御弁１０は、油圧シリンダ１１２内の減衰バルブ１５０に対するバイパス内に設置されてもよい。縮退時に、減衰バルブ１５０では、作動流体室１５８の体積減少分の作動流体が流れる。この作動流体の一部は、減衰バルブ１５０を流れ、作動流体の残部は、減衰力制御弁１０を流れる。このとき、減衰バルブ１５０と減衰力制御弁１０とは互いにバイパスの関係にある。さらに、減衰力制御弁１０は、油圧シリンダ１１２内の減衰バルブ１５０に対するバイパス内に設置されてもよい。伸長時に、減衰バルブ１４８では、作動流体室１６０の体積減少分の作動流体が流れる。この作動流体の一部は、減衰バルブ１４８を流れ、作動流体の残部は、減衰力制御弁１０を流れる。このとき、減衰バルブ１４８と減衰力制御弁１０とは互いにバイパスの関係にある。 Alternatively, damping force control valve 10 may be installed in a bypass to damping valve 150 in hydraulic cylinder 112. At the time of retraction, in the damping valve 150, the working fluid of the volume reduction of the working fluid chamber 158 flows. A portion of the working fluid flows through the damping valve 150, and the remaining portion of the working fluid flows through the damping force control valve 10. At this time, the damping valve 150 and the damping force control valve 10 are in a bypass relationship with each other. Furthermore, damping force control valve 10 may be installed in a bypass to damping valve 150 in hydraulic cylinder 112. At the time of extension, at the damping valve 148, the working fluid of the volume reduction of the working fluid chamber 160 flows. A portion of the working fluid flows through the damping valve 148, and the remaining portion of the working fluid flows through the damping force control valve 10. At this time, the damping valve 148 and the damping force control valve 10 are in a bypass relationship with each other.
　このように、本発明では、減衰力制御弁１０が、油圧シリンダ１１２内において、縮み減衰力を発生させる減衰力発生部（減衰バルブ１５０）に対するバイパス中に設置されてもよく、伸び減衰力を発生させる減衰力発生部（減衰バルブ１４８）に対するバイパス中に設置されてもよく、両方のバイパス中に設置されてもよい。本発明において、減衰力制御弁１０は、減衰力発生部に対するバイパス中に設置されていればよく、減衰力制御弁１０の設置位置及び設置態様は、特に限定されない。 As described above, in the present invention, the damping force control valve 10 may be installed in the hydraulic cylinder 112 in a bypass to the damping force generating portion (damping valve 150) that generates the contraction damping force. It may be placed in a bypass for the damping force generating part (damping valve 148) to be generated, or it may be placed in both bypasses. In the present invention, the damping force control valve 10 may be installed in a bypass for the damping force generation unit, and the installation position and the installation mode of the damping force control valve 10 are not particularly limited.
　また、ショックアブソーバ１００では、通路２１が、弁体２０を軸線方向Ｓに貫通している。しかし、本発明において、通路２１の形成位置は、この例に限定されない。例えば、通路は、軸線方向Ｓに沿って弁体２０の外周側面に形成されていてもよい。また、通路は、弁体２０に形成されていなくてもよい。例えば、通路が、軸線方向Ｓに沿って、弁体２０の外周側面に対向する部材に形成されていてもよい。 Further, in the shock absorber 100, the passage 21 penetrates the valve body 20 in the axial direction S. However, in the present invention, the formation position of the passage 21 is not limited to this example. For example, the passage may be formed on the outer peripheral side surface of the valve body 20 along the axial direction S. Further, the passage may not be formed in the valve body 20. For example, the passage may be formed in a member facing the outer peripheral side surface of the valve body 20 along the axial direction S.
　また、ショックアブソーバ１００では、第一作動流体室３０に、付勢体としてのコイルバネ３４、３５が設置されている。コイルバネ３５は、伸長時に弁体２０に対して第一ポート３０ａに向かう力を加える付勢体である。コイルバネ３４は、縮退時に弁体２０に対して第一ポート３０ａに向かう力を加える付勢体である。本発明では、これら２つの付勢体のいずれか一方が設けられていてもよい。 In the shock absorber 100, coil springs 34 and 35 as biasing members are installed in the first working fluid chamber 30. The coil spring 35 is an urging body that applies a force toward the first port 30 a to the valve body 20 when it is extended. The coil spring 34 is an urging body that applies a force toward the first port 30 a to the valve body 20 during retraction. In the present invention, any one of these two biasing members may be provided.
　上述の実施形態では、円筒状の弁体について説明したが、弁体の形状は上記の例に限定されない。たとえば、弁体が中空角筒形状を有していてもよい。また、油路の形状も上述の例に限定されず、油路の断面が多角形状であってもよく、楕円形状であってもよい。また、本実施形態では、ソレノイドとして、比例ソレノイドが用いられる場合について説明した。但し、本発明は、この例に限定されず、ソレノイドとして、例えば、ＯＮ／ＯＦＦソレノイドが用いられてもよい。 Although the above-mentioned embodiment explained cylindrical valve body, shape of a valve body is not limited to the above-mentioned example. For example, the valve body may have a hollow rectangular tube shape. Further, the shape of the oil passage is not limited to the above example, and the cross section of the oil passage may be polygonal or elliptical. Further, in the present embodiment, the case where a proportional solenoid is used as the solenoid has been described. However, the present invention is not limited to this example, and an ON / OFF solenoid may be used as the solenoid, for example.
　以上、この発明の好ましい実施形態について説明されたが、この発明の範囲および精神を逸脱しない限りにおいて種々の変更が可能であることは明らかである。この発明の範囲は、添付された請求の範囲のみによって限定される。 Although the preferred embodiments of the present invention have been described above, it is apparent that various modifications can be made without departing from the scope and spirit of the present invention. The scope of the present invention is limited only by the appended claims.
１０　減衰力制御弁
２０　弁体
２１　通路
２１ａ　大径部
２１ｂ　連通部
２３　ソレノイドコイル
２６　バルブベッド
３０　第一作動流体室
３０ａ　第一ポート
４０　第二作動流体室
１００　ショックアブソーバ 10 damping force control valve 20 valve body 21 passage 21a large diameter portion 21b communicating portion 23 solenoid coil 26 valve bed 30 first working fluid chamber 30a first port 40 second working fluid chamber 100 shock absorber

Claims (6)

  1. 　ショックアブソーバであって、
    　前記ショックアブソーバは、
    作動流体の流体抵抗により減衰力を発生させる減衰力発生部と、
    前記減衰力発生部に対するバイパス中に配置された減衰力制御弁と
    を備え、
    　前記減衰力制御弁は、
    ソレノイドにより直線往復動する弁体と、
    前記弁体が挿通されるガイド孔と、前記弁体の端面と対向する位置に形成されたポートとを備えた第一作動流体室と、
    前記弁体の前記端面の反対側の端部が露出している第二作動流体室と
    前記弁体の軸線方向に沿って前記弁体に力を加える付勢体と、
    前記第一作動流体室と前記第二作動流体室とを連通する通路と
    を備え、
    　前記弁体の前記端面と前記ポートとの間隙は、作動流体が通過する流路であり、
    　前記流路の開度は、前記弁体の前記端面の位置によって変更され、これにより減衰力が制御され、
    　前記流路の開度が最大になるとき、前記弁体は前記ポートから離れる一方、前記ソレノイドの非通電時に、前記付勢体により、前記弁体の軸線方向に沿って前記ポートに向かう力が、前記弁体に加えられ、これにより、前記弁体が閉位置に移動する。     A shock absorber,
    The shock absorber is
    A damping force generating unit that generates damping force by fluid resistance of the working fluid;
    And a damping force control valve disposed in a bypass to the damping force generation unit,
    The damping force control valve is
    A valve body linearly reciprocated by a solenoid;
    A first working fluid chamber including a guide hole through which the valve body is inserted, and a port formed at a position facing the end face of the valve body;
    A second working fluid chamber in which the opposite end of the end face of the valve body is exposed, and an urging body for applying a force to the valve body along the axial direction of the valve body;
    And a passage communicating the first working fluid chamber with the second working fluid chamber.
    A gap between the end face of the valve body and the port is a flow passage through which the working fluid passes,
    The opening degree of the flow passage is changed by the position of the end face of the valve body, whereby the damping force is controlled,
    When the opening degree of the flow path is maximized, the valve body is separated from the port, and when the solenoid is not energized, the biasing body causes a force toward the port along the axial direction of the valve body by the biasing body. , Added to the valve body, thereby moving the valve body to the closed position.
  2. 　請求項１に記載のショックアブソーバであって、
    　前記通路は、前記弁体の軸線方向に沿って設けられており、前記ソレノイドが通電不能となり前記弁体と前記ポートとの間隔が狭くなるときに、前記第一作動流体室及び前記第二作動流体室のうち、高圧側の作動流体室から低圧側の作動流体室に作動流体を流すことにより、２つの作動流体室の間の圧力差を小さくする。     The shock absorber according to claim 1, wherein
    The passage is provided along the axial direction of the valve body, and the first working fluid chamber and the second operation are operated when the solenoid is not energized and the space between the valve body and the port becomes narrow. By flowing the working fluid from the working fluid chamber on the high pressure side of the fluid chambers to the working fluid chamber on the low pressure side, the pressure difference between the two working fluid chambers is reduced.
  3. 　請求項２に記載のショックアブソーバであって、
    　前記通路は、前記弁体の軸線方向に沿って前記弁体を貫通しており、前記ソレノイドが通電不能となり前記弁体と前記ポートとの間隔が狭くなるときに、前記第一作動流体室と前記第二作動流体室との圧力差を小さくするとともに、前記通路が前記ポートに近づく。     The shock absorber according to claim 2, wherein
    The passage penetrates the valve body along the axial direction of the valve body, and when the solenoid is not energized and the distance between the valve body and the port becomes narrow, The pressure difference with the second working fluid chamber is reduced, and the passage approaches the port.
  4. 　請求項１～３のいずれか１に記載のショックアブソーバであって、
    　前記付勢体は、前記第一作動流体室に設置され、前記弁体に対して、前記弁体の軸線方向に沿って前記ポートに向かう力を加える。     The shock absorber according to any one of claims 1 to 3, wherein
    The biasing body is disposed in the first working fluid chamber, and applies a force to the valve body along the axial direction of the valve body toward the port.
  5. 　請求項１～４のいずれか１に記載のショックアブソーバであって、
    　前記付勢体は、前記弁体の軸線方向において前記付勢体の一部が前記通路と重なる位置に設置され、前記弁体に対して、前記弁体の軸線方向に沿って前記ポートに向かう力を加える。     The shock absorber according to any one of claims 1 to 4, wherein
    The biasing body is disposed at a position where a part of the biasing body overlaps the passage in the axial direction of the valve body, and the valve body is directed to the port along the axial direction of the valve body with respect to the valve body Apply force.
  6. 　請求項１～４のいずれか１に記載のショックアブソーバであって、
    　前記付勢体は、前記弁体の軸線方向において前記付勢体の全部が前記通路と重なる位置に設置され、前記弁体に対して、前記弁体の軸線方向に沿って前記ポートに向かう力を加える。     The shock absorber according to any one of claims 1 to 4, wherein
    The biasing body is disposed at a position where all of the biasing body overlaps the passage in the axial direction of the valve body, and a force directed to the port along the axial direction of the valve body with respect to the valve body Add
PCT/JP2013/053846 2012-02-17 2013-02-18 Shock absorber WO2013122252A1 (en)

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JP2012-033435 2012-02-17
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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111196116A (en) * 2018-11-16 2020-05-26 爱信精机株式会社 Shock absorber

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0579527A (en) * 1991-05-17 1993-03-30 Tokico Ltd Damping force adjusting type hydraulic buffer
WO2011078317A1 (en) * 2009-12-25 2011-06-30 ヤマハ発動機株式会社 Shock absorber

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0579527A (en) * 1991-05-17 1993-03-30 Tokico Ltd Damping force adjusting type hydraulic buffer
WO2011078317A1 (en) * 2009-12-25 2011-06-30 ヤマハ発動機株式会社 Shock absorber

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN111196116A (en) * 2018-11-16 2020-05-26 爱信精机株式会社 Shock absorber
CN111196116B (en) * 2018-11-16 2024-04-09 株式会社爱信 Shock absorber

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