JP2017065471A - Suspension device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a suspension device capable of simplifying pipe arrangement in a low cost.SOLUTION: A suspension device S comprises a 4-port 4-position pressure difference control valve 9, which is disposed among a supply passage 5 connected with a pump 4, a discharge passage 6 connected with a reservoir R, an expansion side passage 7 connected with an expansion side chamber R1 of a damper D, a pressure side passage 8 connected with a pressure side chamber R2 of the damper D, and which rests, when not energized, at a fail position F with the expansion side passage 7, the pressure side passage 8, the supply passage 5 and the discharge passage 6 communicated with each other. Thereby, the suspension device S of the invention can make the damper D function either as an active suspension, or as a semi-active suspension using only the one pressure difference control valve 9, as well as enable a fail safe operation.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a suspension device.

  As this type of suspension device, for example, there is one that functions as an active suspension interposed between a vehicle body and an axle of a vehicle. For example, there is a suspension device filed by the applicant. Specifically, the suspension device includes a damper including a cylinder and a piston that is movably inserted into the cylinder and defines an extension side chamber and a compression side chamber in the cylinder, a pump, a reservoir, an extension side chamber, and a compression side. An electromagnetic switching valve that selectively connects the chamber to the pump and the reservoir, and an electromagnetic pressure control valve that can adjust the pressure of the expansion side chamber and the pressure side chamber that is connected to the pump according to the supply current. (For example, refer to Patent Document 1).

  According to this suspension device, the direction in which the damper exerts thrust is selected by switching the electromagnetic switching valve, and the magnitude of the thrust can be controlled by adjusting the pressure of the electromagnetic pressure control valve.

Japanese Patent Application No. 2014-226734

  As described above, the suspension device described above requires two solenoid valves equipped with solenoids to control the thrust of the damper, increasing the overall cost of the device and reducing the piping of the fluid pressure circuit. There was a problem that handling was complicated.

  In view of this, the present invention was devised in order to improve the above-mentioned problems, and the object thereof is to provide a suspension device that is inexpensive and can simplify the handling of piping.

  In order to solve the above-described object, the suspension device in the problem solving means of the present invention includes a damper, a pump, a reservoir, a supply path connected to the pump, a discharge path connected to the reservoir, and an extension of the damper. An extension side passage connected to the side chamber, a pressure side passage connected to the pressure side chamber of the damper, an extension side damping valve provided in the extension side passage, a pressure side damping valve provided in the pressure side passage, a supply passage, a discharge passage, A 4-port 4-position differential pressure control valve that is provided between the extension side passage and the pressure side passage and that adopts a fail position that communicates the extension side passage, the pressure side passage, the supply passage, and the discharge passage when not energized; And a suction passage connecting the supply passage and the discharge passage, and a suction check valve provided in the middle of the suction passage.

  According to the suspension device of the present invention, the damper can function as an active suspension or a semi-active suspension with only one differential pressure control valve, and a fail-safe operation is also possible.

  Further, in a scene where the thrust is expected to be exhibited, the pump is not necessarily driven, and only needs to be driven when the pump needs to be driven, thereby reducing energy consumption.

  The suspension device of claim 2 includes a damper, a pump, a reservoir, a plurality of fluid pressure circuits, and a shunt valve that distributes the fluid discharged from the pump to each fluid pressure circuit. A supply path connected to the pump, a discharge path connected to the reservoir, an extension side path connected to the extension side chamber of the damper, a pressure side path connected to the pressure side chamber of the damper, and an extension side path An expansion side damping valve, a pressure side damping valve provided in the pressure side passage, and a supply side, a discharge side, an extension side passage, and a pressure side passage. 4-port 4-position differential pressure control valve that adopts fail positions communicating with each other, a supply side check valve provided in the middle of the supply path, a suction path connecting the supply path and the discharge path, and provided in the middle of the suction path And a suction check valve.

  As described above, since the discharge flow rate from the pump is distributed to the fluid pressure circuit provided for each damper using the shunt valve, the flow rate necessary for generating the thrust of each damper can be supplied by one pump. Therefore, only one motor is required to drive the pump for generating the thrust of the plurality of dampers, and only one drive circuit is required to drive the motors. Even if the number of dampers increases, the cost of the entire system can be reduced.

  The suspension device according to claim 3 further includes an extension side damping valve and an extension side check valve provided in parallel to the extension side passage, and a pressure side damping valve and a pressure side check valve provided in parallel to the pressure side passage. Yes.

  Therefore, when supplying the fluid from the pump to the extension side chamber or the pressure side chamber, the fluid can be supplied to the extension side chamber or the pressure side chamber through the extension side check valve or the pressure side check valve with little resistance, and the expansion and contraction direction of the damper is generated. The pump load can be reduced when the direction of thrust coincides. Further, when the fluid is discharged from the extension side chamber or the pressure side chamber, resistance is given to the flow of the fluid that passes through the extension side damping valve or the pressure side damping valve, so that the differential pressure between the extension side chamber and the pressure side chamber is changed to a differential pressure control valve. A large thrust can be obtained by setting the pressure difference to be higher than the pressure difference that can be set in step 1. Even if the thrust force of the solenoid in the differential pressure control valve is reduced, a large thrust force can be generated in the suspension device. Therefore, the differential pressure control valve can be reduced in size and the cost can be further reduced.

  In the suspension device according to claim 4, the differential pressure control valve has an extension side supply position, a pressure side supply position, and a neutral position. Either one is used to control the differential pressure between A port and B port. Therefore, the differential pressure between the A port and the B port can be controlled to a uniquely determined differential pressure, and the thrust of the damper can be appropriately controlled.

  According to the suspension device of the present invention, the thrust of the damper can be controlled only by the differential pressure control valve, so that the overall cost of the device is lower than that of a conventional suspension device that requires two electromagnetic valves. In addition, the piping of the fluid pressure circuit can be simplified.

It is the figure which showed the suspension apparatus in 1st embodiment. It is the figure which interposed the suspension apparatus in 1st embodiment between the vehicle body and the wheel of the vehicle. It is the figure which showed one specific example of the differential pressure | voltage control valve in the suspension apparatus of 1st embodiment. It is the figure which showed the relationship between the electric current supplied to the differential pressure control valve in the suspension apparatus of 1st embodiment, and differential pressure | voltage. It is the figure which showed the characteristic of the thrust at the time of making the suspension apparatus in 1st embodiment function as an active suspension. It is the figure which showed the characteristic of the thrust at the time of making the suspension apparatus in 1st embodiment function as a semi-active suspension. It is the figure which showed the characteristic of the thrust at the time of the failure of the suspension apparatus in 1st embodiment. It is the figure which showed the suspension apparatus in 2nd embodiment. It is the figure which showed the suspension apparatus in 3rd embodiment.

  The present invention will be described below based on the embodiments shown in the drawings. As shown in FIG. 1, the suspension device S in one embodiment includes a cylinder 1 and a piston 2 that is movably inserted into the cylinder 1 and divides the cylinder 1 into an extension side chamber R1 and a pressure side chamber R2. The damper D, the pump 4, the reservoir R connected to the suction side of the pump 4, and the fluid pressure circuit FC provided between the damper D, the pump 4, and the reservoir R are configured.

  The fluid pressure circuit FC is connected to the supply passage 5 connected to the discharge side of the pump 4, the discharge passage 6 connected to the reservoir R, the extension side passage 7 connected to the extension side chamber R1, and the pressure side chamber R2. The pressure side passage 8 to be connected, the extension side damping valve 15 provided in the extension side passage 7, the pressure side damping valve 17 provided in the pressure side passage 8, the supply passage 5, the discharge passage 6, the extension side passage 7 and the pressure side passage 8. 4 port 4 position differential pressure control valve 9 provided in between, and in the middle of the supply path 5 between the differential pressure control valve 9 and the pump 4 from the pump 4 side to the differential pressure control valve 9 side A supply-side check valve 12 that allows only a flow toward the suction passage, a suction passage 10 that connects the discharge passage 6 between the differential pressure control valve 9 and the supply-side check valve 12 in the middle of the supply passage 5, and a suction passage A suction check valve that is provided in the middle of the pipe 10 and allows only the flow of fluid from the discharge path 6 to the supply path 5 It is configured to include a 1 and.

  In the suspension device S, the damper D includes a rod 3 that is movably inserted into the cylinder 1 and connected to the piston 2, and this rod 3 is inserted only into the extension side chamber R1. The damper D is a so-called single rod type damper. 1, the reservoir R is provided independently of the damper D. Although not shown in detail, the reservoir R is provided with an outer cylinder disposed on the outer peripheral side of the cylinder 1 in the damper D. The annular gap between the cylinder 1 and the outer cylinder may be formed.

  To use the suspension device S in a vehicle, as shown in FIG. 2, the cylinder 1 is connected to one of the sprung member BO and unsprung member W of the vehicle, and the rod 3 is connected to the sprung member BO and unsprung member W. What is necessary is just to interpose between the other among them and to interpose between the sprung member BO and the unsprung member W.

  The extension side chamber R1 and the pressure side chamber R2 are filled with, for example, liquid such as hydraulic oil as a fluid, and the reservoir R is also filled with liquid and gas. As the liquid filled in the extension side chamber R1, the pressure side chamber R2, and the reservoir R, for example, a liquid such as water or an aqueous solution can be used in addition to the hydraulic oil. In the present invention, the chamber compressed during the expansion stroke is referred to as an expansion side chamber R1, and the chamber compressed during the contraction stroke is referred to as a compression side chamber R2.

  The pump 4 is set to a one-way discharge type that sucks fluid from the suction side and discharges fluid from the discharge side, and is driven by a motor 13. Various types of motors such as brushless motors, induction motors, synchronous motors and the like can be adopted as the motor 13 regardless of whether they are direct current or alternating current.

  The suction side of the pump 4 is connected to the reservoir R by a pump passage 14, and the discharge side is connected to the supply path 5. Therefore, when driven by the motor 13, the pump 4 sucks liquid from the reservoir R and discharges the liquid to the supply path 5. The discharge path 6 communicates with the reservoir R as described above.

  In the middle of the expansion side passage 7, in addition to the expansion side damping valve 15 that provides resistance to the flow of liquid from the expansion side chamber R1 to the differential pressure control valve 9, the differential pressure control is performed in parallel with the expansion side attenuation valve 15. An extension side check valve 16 that allows only the flow of liquid from the valve 9 toward the extension side chamber R1 is provided. Therefore, since the extension side check valve 16 is kept closed with respect to the flow of the liquid moving from the extension side chamber R1 toward the differential pressure control valve 9, the liquid passes only through the extension side damping valve 15. Then, it flows toward the differential pressure control valve 9 side. The expansion side check valve 16 opens with respect to the flow of the liquid moving from the differential pressure control valve 9 toward the expansion side chamber R 1, and the expansion side check valve 16 has a resistance to the liquid flow as compared with the expansion side damping valve 15. Since it is small, the liquid flows preferentially through the expansion side check valve 16 and flows toward the expansion side chamber R1. The expansion side damping valve 15 may be a throttle valve that allows bidirectional flow, or may be a damping valve such as a leaf valve or a poppet valve that only allows flow from the expansion side chamber R1 toward the differential pressure control valve 9. Good.

  In the middle of the pressure side passage 8, in addition to the pressure side damping valve 17 that provides resistance to the flow from the pressure side chamber R 2 to the differential pressure control valve 9, the pressure side damping valve 17 is connected in parallel with the pressure side damping valve 17. A pressure side check valve 18 that allows only the flow of liquid toward R2 is provided. Therefore, since the pressure side check valve 18 is kept closed with respect to the flow of the liquid moving from the pressure side chamber R2 toward the differential pressure control valve 9, the liquid passes only through the pressure side damping valve 17. It flows toward the differential pressure control valve 9 side. The pressure side check valve 18 opens with respect to the flow of liquid moving from the differential pressure control valve 9 toward the pressure side chamber R2, and the pressure side check valve 18 has a smaller resistance to the liquid flow than the pressure side damping valve 17, The liquid preferentially passes through the pressure side check valve 18 and flows toward the pressure side chamber R2. The pressure side damping valve 17 may be a throttle valve that allows bidirectional flow, or may be a damping valve such as a leaf valve or a poppet valve that allows only the flow from the pressure side chamber R2 toward the differential pressure control valve 9. .

  Further, a suction passage 10 that connects the supply passage 5 and the discharge passage 6 is provided. A suction check valve 11 that allows only the flow of liquid from the discharge path 6 to the supply path 5 is provided in the middle of the suction path 10, and the suction path 10 has a liquid flow from the discharge path 6 to the supply path 5. It is set as a one-way passage that allows only flow.

  A supply side check valve 12 is provided in the middle of the supply path 5 and between the differential pressure control valve 9 and the pump 4. More specifically, a supply side check valve 12 is provided in the middle of the supply path 5 and closer to the pump 4 than the connection point of the suction passage 10. The supply side check valve 12 controls the differential pressure from the pump 4 side. Only the flow toward the valve 9 is allowed, and the opposite flow is blocked. Therefore, even if the pressure on the differential pressure control valve 9 side becomes higher than the discharge pressure of the pump 4, the supply side check valve 12 is closed so that the liquid does not flow backward to the pump 4 side.

  The differential pressure control valve 9 is connected to the A port a connected to the expansion side passage 7, the B port b connected to the pressure side passage 8, the P port p connected to the supply passage 5, and the discharge passage 6. The T-port t has four ports to control the differential pressure between the A-port a and the B-port b, and to communicate with the expansion-side passage 7, the pressure-side passage 8, the supply passage 5 and the discharge passage 6 when not energized. It is a 4-port 4-position electromagnetic differential pressure control valve that takes a position.

  Specifically, the A-side supply position X that connects the A port a and the P port p and the B port b and the T port t, and the A port a, B port b, P port p, and T port t Neutral position N that allows all ports to communicate with each other, pressure side supply position Y that communicates A port a and T port t and B port b and P port p, and all ports a, b, p, and t A spool SP having a fail position F that communicates with each other, a spring Cs that urges the spool SP, and a solenoid Sol that provides the spool SP with a thrust force that opposes the spring Cs are provided. That is, at the extension side supply position X, the supply path 5 is communicated with the extension side passage 7 and the discharge path 6 is communicated with the pressure side path 8. At the neutral position N and the fail position F, the supply path 5 and the discharge path 6 are communicated. The expansion side passage 7 and the pressure side passage 8 are communicated with each other. At the pressure side supply position Y, the supply passage 5 is communicated with the pressure side passage 8 and the discharge passage 6 is communicated with the expansion side passage 7. The extension side supply position X, the neutral position N, and the pressure side supply position Y are continuously switched by the movement of the spool SP.

Further, the pressure from the extension side passage 7 is guided to one end side of the spool SP as a pilot pressure, and the spool SP can be urged downward in FIG. 1 by the pressure of the extension side passage 7. Further, the pressure from the pressure side passage 8 is guided to the other end side of the spool SP as a pilot pressure, and the spool SP can be biased upward in FIG. The force that pushes the spool SP downward in FIG. 1 by the pressure of the extension side passage 7 and the force that pushes the spool SP upward in FIG. 1 by the pressure of the compression side passage 8 are forces that push the spool SP in the opposite direction. These resultant forces are used as fluid pressure feedback force. When the solenoid Sol is energized, the spool SP balances the thrust from the solenoid Sol among the positions X, Y, and N, the fluid pressure feedback force due to the pressure of the expansion side passage 7 and the pressure side passage 8, and the biasing force of the spring Cs. Accordingly, the position is switched to any one of the extension side supply position X, the neutral position N, and the compression side supply position Y. The position of the spool SP in which the thrust, the fluid pressure feedback force, and the urging force of the spring Cs are balanced changes depending on the magnitude of the thrust of the solenoid Sol. The pressure can be controlled. In this way, the differential pressure control valve 9 has the expansion side supply position X, the pressure side supply position Y, and the neutral position N. When energized, the expansion side supply position X, the pressure side supply position Y, and the neutral position are supplied by fluid pressure feedback. Any one of the positions N can be used to control the differential pressure between the A port a and the B port b to a uniquely determined differential pressure.
On the other hand, when no power is supplied to the solenoid Sol, the spool SP is pushed by the spring Cs and takes the fail position F. In this example, the expansion side passage 7 is connected to the A port a and the compression side passage 8 is connected to the B port b. However, the expansion side passage 7 is connected to the B port b, and the compression side passage 8 is connected to the A port. You may connect to a.

  Specifically, for example, as shown in FIG. 3, the differential pressure control valve 9 includes a spool SP, a housing H into which the spool SP is axially movable, and a reaction force pin accommodated in the housing H. P, a spring Cs that is a coil spring that biases the spool SP from one end side toward the other end side (left side to right side in FIG. 3), and the spool SP from the other end side to one end side (left side from right side in FIG. 3) ) And a solenoid Sol that can exert a thrust to be pushed toward.

  As shown in FIG. 3, the spool SP is cylindrical and has four lands 40, 41, 42, 43 on the outer periphery, three grooves 44, 45, 46 provided between the lands, and the center of the left end. A vertical hole 47 that opens and a horizontal hole 48 that extends in the radial direction from the tip of the vertical hole 47 and communicates with the rightmost groove 46 are configured. The outer diameters of the lands 40, 41, 42, 43 are set to the same diameter.

  The reaction force pin P includes a disk-shaped base 50 and a shaft 51 that extends from the center of the right end of the base 50 and is slidably inserted into the vertical hole 47 of the spool SP. The shaft portion 51 is set to a length that does not obstruct the stroke in the left-right direction, which is the axial direction of the spool SP, and does not come out of the vertical hole 47 during the stroke of the spool SP. Further, the shaft portion 51 is inserted into the vertical hole 47 to close the outlet end of the vertical hole 47, and the vertical hole 47 functions as the pressure chamber Pr3.

  The housing H has a bottomed cylindrical shape, and an inner peripheral diameter is set to a diameter that allows sliding contact with the outer periphery of the lands 40, 41, 42, 43. A spool SP is slidably inserted into the housing H, and the spool SP can move in the horizontal direction in FIG. By inserting the spool SP into the housing H, pressure chambers Pr1 and Pr2 are formed in the housing H on both sides of the spool SP. Further, four recesses 60, 61, 62, 63 formed by annular grooves are provided on the inner periphery of the housing H, and a base portion 50 of the reaction force pin P is provided at the bottom of the left end in FIG. It is mated.

  Further, a spring Cs is interposed between the base 50 of the reaction force pin P and the spool SP, and the spool SP is urged rightward in FIG. 3 by the spring Cs.

  A solenoid Sol is attached to the right end opening end of the housing H, and a plunger PP in the solenoid Sol is brought into contact with the right end of the spool SP so that the thrust of the solenoid Sol acts on the spool SP.

  Further, the housing H has a port 64 connected to the extension side passage 7 and corresponding to the A port, a port 65 connected to the pressure side passage 8 and corresponding to the B port, and a port 65 connected to the supply passage 5 and connected to the P port. Corresponding ports 66, 67, ports 68, 69 connected to the discharge path 6 and corresponding to the T port, and connected to the port 64, the expansion side passage 7 communicates with the pressure chambers Pr1, Pr2 on both sides of the spool SP. A communication path 70 is provided.

  The port 64 opens from the outer periphery of the housing H and communicates between the recesses 61 and 62 on the inner periphery of the housing H. The port 65 opens from the outer periphery of the housing H and is the inner periphery of the housing H and communicates between the recesses 62 and 63. The port 66 opens from the outer periphery of the housing H and communicates with the recess 62. The port 67 branches from the port 66 and communicates with the recess 60. The port 68 opens from the outer periphery of the housing H and communicates with the recess 61. The port 69 branches from the port 68 and communicates with the recess 63.

  The differential pressure control valve 9 shown in FIG. 3 is configured as described above. FIG. 3 shows a state in which the spool SP is arranged at the neutral position N. Even if the spool SP strokes at the maximum width, the land 40 and the land 43 are in sliding contact with the inner periphery of the housing H, so that the pressure chambers Pr1, Pr2 do not communicate with the recesses 60, 61, 62, 63. . The pressure in the extension side passage 7 is guided to the pressure chamber Pr1 and the pressure chamber Pr2 through the communication passage 70. The pressure in the pressure chamber Pr1 acts on the left end of the spool SP in FIG. 3 with an area obtained by subtracting the cross-sectional area of the shaft portion 51 of the reaction force pin P from the cross-sectional area of the spool SP. Conversely, the pressure in the pressure chamber Pr2 acts on the right end of the spool SP in FIG. 3 with the cross-sectional area of the spool SP as the pressure receiving area. Therefore, the spool SP is urged to the left in FIG. 3 by a force obtained by multiplying the pressure of the extension side passage 7 by the cross-sectional area of the shaft portion 51. On the other hand, the pressure in the pressure side passage 8 is guided through the port 65 into the pressure chamber Pr3 formed by the vertical hole 47 of the spool SP. Therefore, the spool SP is urged to the right in FIG. 3 by a force obtained by multiplying the pressure of the pressure side passage 8 by the cross-sectional area of the shaft portion 51. That is, with the cross-sectional area of the shaft portion 51 as the pressure receiving area, the pressure in the extension side passage 7 and the pressure in the pressure side passage 8 act so as to push the spool SP in opposite directions.

  At the neutral position N, the land 41 faces the inner periphery of the housing H between the recesses 60 and 61, and the communication between the recess 60 and the recess 61 is interrupted. On the other hand, since the lands 41 and 42 are the inner periphery of the housing H and do not slide between the recesses 61 and 62 and between the recesses 62 and 63, the recesses 61, 62, and 63 are communicated with each other. Further, since the lands 41 and 42 are the inner periphery of the housing H and do not slide between the recesses 61 and 62 and between the recesses 62 and 63, the ports 64 and 65 are opened. Therefore, the ports 64 and 65 communicate with the ports 68 and 69 through the recesses 61 and 63 and communicate with the port 66 through the recess 62, so that the supply path 5, the discharge path 6, the expansion side path 7, and the pressure side The passages 8 communicate with each other.

  When the spool SP moves to the right from the position shown in FIG. 3, the land 41 faces the inner periphery between the recesses 61 and 62 of the housing H, the communication between the recess 61 and the recess 62 is cut off, and the land 42 is the recess of the housing H. The recess 62 and the recess 63 are disconnected from each other while facing the inner periphery between 62 and 63. Then, the port 64 and the port 66 are communicated, and the port 65 and the port 69 are communicated. In this state, the supply passage 5 and the expansion side passage 7 are communicated, and the discharge passage 6 and the pressure side passage 8 are communicated, so that the differential pressure control valve 9 takes the expansion side supply position X.

  On the other hand, when the spool SP moves to the left from the position shown in FIG. 3, the land 42 faces the inner periphery between the recesses 61 and 62 of the housing H, and the communication between the recess 61 and the recess 62 is cut off. The recess 62 and the recess 63 are disconnected from each other, facing the inner periphery between the recesses 62 and 63. Then, the port 65 and the port 66 are communicated, and the port 64 and the port 68 are communicated. In this state, the supply passage 5 and the pressure side passage 8 are communicated, and the discharge passage 6 and the expansion side passage 7 are communicated, so that the differential pressure control valve 9 takes the pressure side supply position Y.

  As shown in FIG. 4, when the solenoid Sol is energized and the amount of current flowing through the solenoid Sol becomes IM, the spool SP is positioned at the neutral position N shown in FIG. During normal control, the amount of current is supplied in the range from IL to IH in FIG.

  The flow rate supplied from the pump 4 to the supply path 5 and the port 66 flows from the recess 62 through the groove 45 and the recess 61 to the reservoir R via the port 68 and the discharge path 6, and from the recess 62 to the groove 46. Then, the flow is divided into the flow returning to the reservoir R through the recess 63 through the port 69 and the discharge path 6. The flow path areas in the flow path formed by the recess 62 and the land 42, the recess 61 and the land 41, and the recess 63 and the land 43 are equal, and the pressure loss generated there is also equal. Therefore, the pressure Pa of the port 64 corresponding to the A port facing the groove 45 is equal to the pressure Pb of the port 65 corresponding to the B port facing the groove 46. Therefore, at the neutral position N, the fluid pressure feedback force acting on the spool SP is 0, and is balanced only by the thrust of the solenoid Sol and the urging force of the spring Cs.

  When the amount of current supplied to the solenoid Sol becomes smaller than IM, the balance of force is lost, and the spool SP temporarily moves rightward from the position shown in FIG. Then, the flow path area formed by the land 43 and the recess 63 is increased, the pressure loss in the route from the pressure side path 8 to the discharge path 6 is reduced, and the flow path area formed by the land 41 and the recess 61 is decreased. The pressure loss in the route from the extension side passage 7 to the discharge passage 6 increases. Therefore, Pa> Pb. As a result, the pressure in the expansion side passage 7 increases, the pressure in the compression side passage 8 decreases, and a fluid pressure feedback force acts in the left direction in FIG. 3, and finally the thrust of the solenoid Sol and the attachment of the spring Cs are applied. The spool SP stops at a position where the force and the fluid pressure feedback force are balanced.

  When the amount of current supplied to the solenoid Sol becomes larger than IM, the balance of force is lost, and the spool SP temporarily moves to the left from the position shown in FIG. Then, the flow path area formed by the lands 43 and the recesses 63 decreases, the pressure loss in the route from the pressure side passage 8 to the discharge path 6 increases, and the flow path area formed by the lands 41 and the recesses 61 increases. The pressure loss in the route from the extension side passage 7 to the discharge passage 6 is reduced. Therefore, Pa <Pb. As a result, the pressure in the compression side passage 8 increases, the pressure in the expansion side passage 7 decreases, and a fluid pressure feedback force acts in the right direction in FIG. 3, and finally the thrust of the solenoid Sol and the attachment of the spring Cs. The spool SP stops at a position where the force and the fluid pressure feedback force are balanced.

  Therefore, the differential pressure between the pressure in the extension side passage 7 and the pressure in the pressure side passage 8 can be controlled by adjusting the amount of current supplied to the solenoid Sol. When the damper D expands and contracts, the liquid enters and exits the expansion side chamber R1 and the pressure side chamber R2 of the damper D. Therefore, the flow rate passing through the differential pressure control valve 9 increases or decreases from the pump flow rate by the flow rate due to the expansion and contraction of the damper D. Thus, even if the flow rate increases or decreases due to the expansion and contraction of the damper D, the spool SP automatically moves due to the fluid pressure feedback force, and the differential pressure is a difference uniquely determined by the amount of current supplied to the solenoid Sol. Controlled by pressure.

  The pressure difference between the pressure in the extension side passage 7 and the pressure in the pressure side passage 8 can be appropriately controlled when the pressure on the high pressure side is kept higher than the reservoir pressure and the pump flow rate is insufficient, or the pump In a state where 4 is stopped and liquid must be supplied from the reservoir R through the suction check valve 11, the differential pressure is zero.

  The suspension device S is configured as described above. Next, the operation thereof will be described. First, the normal operation in which the motor 13, the pump 4, and the differential pressure control valve 9 are normally operated will be described.

  Basically, if the pump 4 is driven by the motor 13 and the differential pressure between the expansion chamber R1 and the compression chamber R2 is controlled by the differential pressure control valve 9, the damper D can function as an actuator that actively expands or contracts. . When the thrust generated in the damper D is in the extension direction of the damper D, the differential pressure control valve 9 is set to the pressure side supply position Y, the pressure side chamber R2 is connected to the supply path 5, and the extension side chamber R1 is connected to the reservoir R. On the other hand, when the thrust generated in the damper D is in the contraction direction of the damper D, the differential pressure control valve 9 is set to the expansion side supply position X, the expansion side chamber R1 is connected to the supply path 5, and the pressure side chamber R2 is connected to the reservoir R. Connect to. If the differential pressure between the expansion chamber R1 and the compression chamber R2 is adjusted by the differential pressure control valve 9, the magnitude of thrust in the extension direction or contraction direction of the damper D can be controlled.

  In controlling the thrust, for example, as shown in FIG. 2, information that can grasp the vibration state of the vehicle necessary for a control law suitable for vehicle vibration suppression, for example, the vertical direction of the sprung member BO and the unsprung member W Vehicle information such as information such as acceleration and speed and information such as the expansion and contraction speed and expansion acceleration of the damper D is obtained, and the target thrust to be generated in the damper D is determined according to the control law, and the thrust is applied to the damper D according to the target thrust. Controller C that determines the amount of current to be applied to the differential pressure control valve 9 and the amount of current to be applied to the motor 13 that drives the pump 4, as received by the controller C in response to a command from the controller C A driver Dr that supplies current to the differential pressure control valve 9 and the motor 13 may be provided. The driver Dr includes, for example, a drive circuit that PWM drives the solenoid Sol in the differential pressure control valve 9 and a drive circuit that PWM drives the motor 13. When the driver Dr receives a command from the controller C, the driver Dr supplies current to the solenoid Sol and the motor 13 as determined by the controller C. Since the thrust of the damper D is controlled by the differential pressure control valve 9, when the pump 4 is driven by the motor 13, it is only necessary that the pump 4 can be rotationally driven at a constant rotational speed. Each drive circuit in the driver Dr may be a drive circuit other than the drive circuit that performs PWM driving. When the target thrust generated by the damper D is the extension direction of the damper D, the driver Dr supplies a current less than the current amount IM to the solenoid Sol of the differential pressure control valve 9 according to the thrust of the damper D. On the contrary, when the target thrust generated in the damper D is the contraction direction of the damper D, the driver Dr supplies a current exceeding the current amount IM to the solenoid Sol of the differential pressure control valve 9 according to the thrust of the damper D. As a control law used for thrust control in the suspension device S, a control law suitable for the vehicle may be selected. For example, a control law excellent in vehicle vibration suppression such as skyhook control may be employed. In this case, the controller C and the driver Dr are described as separate units, but the suspension device S may be controlled by a single control device having the functions of the controller C and the driver Dr. The information input to the controller C may be information suitable for the control law adopted by the controller C. Although not shown, the information may be detected by a sensor or the like and input to the controller C.

  The operation in the case where the damper D is actively expanded and contracted has been described above. However, while the vehicle is traveling, the damper D expands and contracts due to disturbance due to the unevenness of the road surface. The operation based on the points to be described will be described.

  When the damper D expands and contracts due to a disturbance, four cases can be considered if the damper D is divided into the direction in which thrust is generated and the expansion and contraction direction of the damper D. When the pressure of the A port a is Pa and the pressure of the B port b is Pb, as a first case, control is performed so that Pa> Pb, and the suspension device S exerts a thrust force that pushes the piston 2 downward. A case where the damper D is extended by an external force will be described. The volume of the expansion side chamber R1 decreases due to the extension of the damper D, and the liquid discharged from the expansion side chamber R1 flows through the expansion side damping valve 15 and flows into the A port a of the differential pressure control valve 9. On the other hand, the expansion of the damper D expands the volume of the pressure side chamber R2, and the pressure side chamber R2 is replenished with liquid from the pump 4 via the B port b and the pressure side check valve 18.

  When the extension speed increases and the liquid flow rate to be replenished to the pressure side chamber R2 exceeds the discharge flow rate of the pump 4, the liquid is also supplied from the reservoir R via the suction check valve 11. Since the differential pressure between the pressure Pa of the A port a and the pressure Pb of the B port b is kept constant by the differential pressure control valve 9, the pressure in the expansion side chamber R 1 is equal to the pressure loss caused by the expansion side damping valve 15. It becomes higher than the pressure of a. Therefore, the pressure in the expansion side chamber R1 becomes higher than the pressure side chamber R2 by a value obtained by adding the pressure corresponding to the pressure loss generated in the expansion side damping valve 15 to the differential pressure adjusted by the differential pressure control valve 9, and the damper D is Demonstrate thrust to suppress elongation. The characteristics of the expansion / contraction speed of the damper and the thrust exerted at this time are shown in FIG. 5 in the graph in which the vertical axis represents the thrust of the damper D and the horizontal axis represents the expansion / contraction speed of the damper D. The characteristic indicated by the line (1) is obtained.

  As a second case, a case will be described in which Pa> Pb is controlled to cause the suspension device S to exert a thrust force that pushes down the piston 2 and the damper D is contracted by an external force. The volume of the pressure side chamber R2 decreases due to the contraction of the damper D, and the liquid discharged from the pressure side chamber R2 passes through the pressure side damping valve 17 and flows to the B port b of the differential pressure control valve 9. On the other hand, the volume of the extension side chamber R1 expands due to the contraction of the damper D, and the extension side chamber R1 is replenished with the liquid from the pump 4 through the A port a through the extension side check valve 16. Since the differential pressure between the pressure Pa of the A port a and the pressure Pb of the B port b is kept constant by the differential pressure control valve 9, the pressure in the pressure side chamber R 2 is equal to the pressure loss caused by the pressure side damping valve 17. It becomes higher than the pressure of b. Therefore, the pressure in the expansion side chamber R1 becomes higher than the pressure side chamber R2 by a value obtained by subtracting the pressure loss generated in the pressure side damping valve 17 from the differential pressure adjusted by the differential pressure control valve 9, and the damper D contracts. Demonstrate thrust to subsidize. The characteristics of the expansion / contraction speed of the damper and the thrust exerted at this time are the characteristics indicated by the line (2) in FIG.

  Further, when the contraction speed is increased and the liquid flow rate to be replenished to the expansion side chamber R1 exceeds the discharge flow rate of the pump 4, the liquid is also supplied from the reservoir R via the suction check valve 11. In such a state, the A port a cannot be pressurized at the discharge flow rate of the pump 4, and the pressure Pa of the A port a becomes slightly lower than the pressure of the reservoir R, and the pressure difference of the A port a is controlled by the differential pressure control valve 9. The differential pressure between the pressure Pa and the pressure Pb at the B port b cannot be controlled, and the differential pressure between the two becomes zero. Then, the damper D exerts a thrust by the differential pressure between the expansion side chamber R1 and the pressure side chamber R2 caused by the pressure loss generated when the liquid discharged from the pressure side chamber R2 passes through the pressure side damping valve 17. The characteristics of the expansion / contraction speed of the damper and the thrust exerted at this time are the characteristics indicated by the line (3) in FIG. 5 and are discontinuous with the characteristics indicated by the line (2). As described above, when the liquid flow rate to be replenished to the extension side chamber R1 exceeds the discharge flow rate of the pump 4, the damper D functions as a passive damper, and the thrust changes depending on the contraction speed.

  Next, as a third case, the control is performed so that Pb> Pa, and the suspension device S exerts a thrust force that pushes the piston 2 upward, and the damper D is contracted by an external force. explain. The volume of the pressure side chamber R2 decreases due to the contraction of the damper D, and the liquid discharged from the pressure side chamber R2 passes through the pressure side damping valve 17 and flows to the B port b of the differential pressure control valve 9. On the other hand, the volume of the extension side chamber R1 expands due to the contraction of the damper D, and the extension side chamber R1 is replenished with liquid from the reservoir R through the A port a through the extension side check valve 16.

  Since the differential pressure between the pressure Pa of the A port a and the pressure Pb of the B port b is kept constant by the differential pressure control valve 9, the pressure in the pressure side chamber R2 is equal to the B port b by the pressure loss generated in the pressure side damping valve 17. Higher than the pressure. Therefore, the pressure in the pressure side chamber R2 becomes higher than the expansion side chamber R1 by a value obtained by adding the pressure corresponding to the pressure loss generated in the pressure side damping valve 17 to the differential pressure adjusted by the differential pressure control valve 9, and the damper D contracts. Demonstrate thrust to suppress The characteristics of the expansion / contraction speed of the damper and the thrust exerted at this time are the characteristics indicated by the line (4) in FIG.

  As a fourth case, a case will be described in which Pb> Pa is controlled to cause the suspension device S to exert a thrust force that pushes the piston 2 upward, and the damper D is extended by an external force. The volume of the expansion side chamber R1 decreases due to the extension of the damper D, and the liquid discharged from the expansion side chamber R1 flows through the expansion side damping valve 15 and flows into the A port a of the differential pressure control valve 9. On the other hand, the expansion of the damper D expands the volume of the pressure side chamber R2, and the pressure side chamber R2 is replenished with liquid from the pump 4 via the B port b and the pressure side check valve 18. Since the differential pressure between the pressure Pa of the A port a and the pressure Pb of the B port b is kept constant by the differential pressure control valve 9, the pressure in the expansion side chamber R 1 is equal to the pressure loss caused by the expansion side damping valve 15. It becomes higher than the pressure of port a. Therefore, the pressure in the compression side chamber R2 becomes higher than the expansion side chamber R1 by the value obtained by subtracting the pressure loss generated in the expansion side damping valve 15 from the differential pressure adjusted by the differential pressure control valve 9, and the damper D is Demonstrate the thrust to support elongation. The characteristics of the expansion / contraction speed of the damper and the thrust exerted at this time are the characteristics indicated by the line (5) in FIG.

  Further, when the extension speed is increased and the liquid flow rate to be replenished to the pressure side chamber R2 exceeds the discharge flow rate of the pump 4, the liquid is also supplied from the reservoir R via the suction check valve 11. In such a state, the B port b cannot be pressurized at the discharge flow rate of the pump 4, and the pressure Pb of the B port b becomes slightly lower than the pressure of the reservoir R, and the pressure difference of the A port a is controlled by the differential pressure control valve 9. The differential pressure between the pressure Pa and the pressure Pb at the B port b cannot be controlled, and the differential pressure between the two becomes zero. Then, the damper D exerts thrust by the differential pressure between the expansion side chamber R1 and the compression side chamber R2 caused by the pressure loss generated when the liquid discharged from the expansion side chamber R1 passes through the expansion side damping valve 15. The characteristics of the expansion / contraction speed of the damper and the thrust exerted at this time are the characteristics indicated by the line (6) in FIG. 5, and are discontinuous with the characteristics indicated by the line (5). As described above, when the liquid flow rate to be replenished to the pressure side chamber R2 exceeds the discharge flow rate of the pump 4, the damper D functions as a passive damper, and the thrust changes depending on the extension speed.

  The damper D exhibits a characteristic that the thrust changes from the line (2) in FIG. 5 to the line (3) on the contraction side, and the thrust changes from the line (5) to the line (6) in FIG. Although the characteristic is shown, the change in the characteristic occurs very instantaneously, and the influence on the ride comfort is slight.

  From the above, by the differential pressure control by the differential pressure control valve 9, in FIG. 5, the line between the line (1) to the line (3) to the line (4) to the line (6) is connected. The thrust of the damper D can be varied within the range. Further, when the discharge flow rate of the pump 4 is supplied to the expansion side chamber R1 and the compression side chamber R2 by driving the pump 4, the discharge flow rate of the pump 4 is larger than the volume increase amount of the expansion chamber. In some cases, thrust can be exerted in the same direction as the expansion and contraction direction of the damper D.

  Next, the operation of the suspension device S when the pump 4 is stopped and not driven will be described. Also in this case, four cases can be considered if the direction in which the damper D is expanded and contracted by a disturbance and the direction in which the damper D generates a thrust are divided into cases.

  As a first case, a case will be described in which Pa> Pb is controlled to cause the suspension device S to exert a thrust force that pushes the piston 2 downward, and the damper D is extended by an external force. The volume of the expansion side chamber R1 decreases due to the extension of the damper D, and the liquid discharged from the expansion side chamber R1 flows through the expansion side damping valve 15 and flows into the A port a of the differential pressure control valve 9. On the other hand, the expansion of the damper D expands the volume of the pressure side chamber R2, and the pressure side chamber R2 is replenished from the reservoir R via the pressure port check valve 18 via the B port b.

  Since the differential pressure between the pressure Pa of the A port a and the pressure Pb of the B port b is kept constant by the differential pressure control valve 9, the pressure in the expansion side chamber R 1 is equal to the pressure loss caused by the expansion side damping valve 15. It becomes higher than the pressure of a. Therefore, the pressure in the expansion side chamber R1 becomes higher than the pressure side chamber R2 by a value obtained by adding the pressure corresponding to the pressure loss generated in the expansion side damping valve 15 to the differential pressure adjusted by the differential pressure control valve 9, and the damper D is Demonstrate thrust to suppress elongation. The characteristics of the expansion / contraction speed of the damper and the thrust exerted at this time are shown in FIG. 6 in the graph in which the vertical axis represents the thrust of the damper D and the horizontal axis represents the expansion / contraction speed of the damper D. The characteristic indicated by the line (1) is obtained.

  As a second case, a case will be described in which Pa> Pb is controlled to cause the suspension device S to exert a thrust force that pushes down the piston 2 and the damper D is contracted by an external force. The volume of the pressure side chamber R2 decreases due to the contraction of the damper D, and the liquid discharged from the pressure side chamber R2 passes through the pressure side damping valve 17 and flows to the B port b of the differential pressure control valve 9. On the other hand, the volume of the expansion side chamber R1 expands due to the contraction of the damper D, and the expansion side chamber R1 is replenished with liquid from the reservoir R through the suction check valve 11 and the A port a through the expansion side check valve 16. The pressure Pa of the A port a is slightly lower than the pressure of the reservoir R, and the differential pressure control valve 9 cannot control the differential pressure between the pressure Pa of the A port a and the pressure Pb of the B port b. 0. Then, the damper D exerts a thrust by the differential pressure between the expansion side chamber R1 and the pressure side chamber R2 caused by the pressure loss generated when the liquid discharged from the pressure side chamber R2 passes through the pressure side damping valve 17. The characteristics of the expansion / contraction speed of the damper and the thrust exerted at this time are the characteristics indicated by the line (2) in FIG.

  Next, as a third case, the control is performed so that Pb> Pa, and the suspension device S exerts a thrust force that pushes the piston 2 upward, and the damper D is contracted by an external force. explain. The volume of the pressure side chamber R2 decreases due to the contraction of the damper D, and the liquid discharged from the pressure side chamber R2 passes through the pressure side damping valve 17 and flows to the B port b of the differential pressure control valve 9. On the other hand, the volume of the extension side chamber R1 expands due to the contraction of the damper D, and the extension side chamber R1 is replenished with liquid from the reservoir R through the A port a through the extension side check valve 16.

  Since the differential pressure between the pressure Pa of the A port a and the pressure Pb of the B port b is kept constant by the differential pressure control valve 9, the pressure in the pressure side chamber R2 is equal to the B port b by the pressure loss generated in the pressure side damping valve 17. Higher than the pressure. Therefore, the pressure in the pressure side chamber R2 becomes higher than the expansion side chamber R1 by a value obtained by adding the pressure corresponding to the pressure loss generated in the pressure side damping valve 17 to the differential pressure adjusted by the differential pressure control valve 9, and the damper D contracts. Demonstrate thrust to suppress The characteristics of the expansion / contraction speed of the damper and the thrust exerted at this time are the characteristics indicated by the line (3) in FIG.

  As a fourth case, a case will be described in which Pb> Pa is controlled to cause the suspension device S to exert a thrust force that pushes the piston 2 upward, and the damper D is extended by an external force. The volume of the expansion side chamber R1 decreases due to the extension of the damper D, and the liquid discharged from the expansion side chamber R1 flows through the expansion side damping valve 15 and flows into the A port a of the differential pressure control valve 9. On the other hand, the volume of the pressure side chamber R2 expands due to the extension of the damper D, and the pressure side chamber R2 is replenished with liquid from the reservoir R through the suction check valve 11 and the B port b through the pressure side check valve 18. The pressure Pb of the B port b is slightly lower than the pressure of the reservoir R, and the differential pressure control valve 9 cannot control the differential pressure between the pressure Pa of the A port a and the pressure Pb of the B port b. 0. Then, the damper D exerts thrust by the differential pressure between the expansion side chamber R1 and the compression side chamber R2 caused by the pressure loss generated when the liquid discharged from the expansion side chamber R1 passes through the expansion side damping valve 15. The characteristics of the expansion / contraction speed of the damper and the thrust exerted at this time are the characteristics indicated by the line (4) in FIG.

  Therefore, in the state where the pump 4 is stopped, the differential pressure control by the differential pressure control valve 9 causes the first quadrant in FIG. 6 to fall within the third quadrant within the range from the line (1) to the line (4). Then, the thrust of the damper D can be made variable in the range from the line (3) to the line (2).

  In addition, when the pump 4 is stopped, when the suspension device S is to exert a thrust force that pushes down the piston 2 downward, when the damper D is contracted by an external force, the differential pressure control valve 9 does not depend on the differential pressure control, The thrust of the damper D has a characteristic indicated by a line (2) in FIG. This brings about an effect equivalent to controlling the compression side damping force to the lowest damping force in the damping force variable damper. Furthermore, when the pump 4 is stopped, when the suspension device S tries to exert a thrust force that pushes the piston 2 upward, when the damper D is extended by an external force, the differential pressure control valve 9 does not depend on the differential pressure control, The thrust of the damper D has a characteristic indicated by a line (4) in FIG. This brings about an effect equivalent to controlling the extension side damping force to the lowest damping force in the damping force variable damper.

  Here, in the case of a semi-active suspension, consider a case where skyhook control is executed according to the Karnop law using a damping force variable damper. When the extension side damping force (force in the direction of pushing down the piston) is required, the damping force of the damping force variable damper is controlled to the damping force that can obtain the target thrust during extension operation, and the extension side damping force is obtained during contraction operation. It is controlled so that the lowest damping force is exerted on the compression side. On the other hand, when a compression side damping force (force in the direction of pushing up the piston) is required, the damping force of the damping force variable damper is controlled to a damping force that can obtain the target thrust during the contraction operation, and a compression side damping force is obtained during the extension operation. It is controlled so as to exhibit the lowest damping force toward the extension side. In the suspension device S of the present invention, when the damper D exerts a thrust force that pushes down the piston 2 while the pump 4 is stopped, the thrust force of the damper D is controlled within the output possible range by the differential pressure control valve 9 at the time of extension and contracts. Sometimes the damper D exhibits the lowest thrust. On the other hand, in the suspension device S of the present invention, when the damper D exerts a thrust force that pushes up the piston 2 while the pump 4 is stopped, the thrust force of the damper D is controlled by the differential pressure control valve 9 within a possible output range during contraction. The damper D exhibits the lowest thrust when extended. Therefore, the suspension device S of the present invention can automatically exhibit the same function as the semi-active suspension when the pump 4 is stopped. Therefore, even if the pump 4 is being driven, the suspension device S can automatically function as a semi-active suspension if the discharge flow rate of the pump 4 becomes less than the volume increase amount of the expansion side chamber R1 or the compression side chamber R2.

  Finally, the operation of the suspension apparatus S when the energization of the motor 13 and the differential pressure control valve 9 of the suspension apparatus S is not possible due to some abnormality will be described. Such failures include, for example, when the motor 13 and the differential pressure control valve 9 cannot be energized, and when the controller C and the driver Dr are abnormal, the motor 13 and the differential pressure control valve 9 are energized. This includes the case of stopping.

  At the time of failure, energization to the motor 13 and the differential pressure control valve 9 is stopped or cannot be energized, the pump 4 is stopped, and the differential pressure control valve 9 is urged by the spring Cs to fail. Position F is taken.

  In this state, when the damper D is extended by an external force, the volume of the extension side chamber R1 is reduced, so that the reduced fluid is discharged from the extension side chamber R1 through the extension side damping valve 15. The pressure side chamber R2 whose volume is expanded is replenished with liquid from the expansion side chamber R1 and the reservoir R.

  Therefore, the pressure in the expansion side chamber R1 is higher than the pressure in the compression side chamber R2 by the amount of pressure loss that occurs when the fluid discharged from the expansion side chamber R1 passes through the expansion side damping valve 15, and the damper D is in the expansion side chamber R1. The thrust is exerted by the differential pressure between the pressure side chamber R2. The characteristics of the expansion / contraction speed of the damper and the thrust exerted at this time are the characteristics indicated by the line (1) in FIG.

  On the other hand, when the damper D is contracted by an external force, the volume of the pressure side chamber R2 is reduced, so that the reduced fluid is discharged from the pressure side chamber R2 through the pressure side damping valve 17. The expansion side chamber R1 whose volume is expanded is replenished with liquid from the pressure side chamber R2 and the reservoir R.

  Therefore, the pressure in the pressure side chamber R2 becomes higher than the pressure in the expansion side chamber R1 by the pressure loss generated when the fluid discharged from the pressure side chamber R2 passes through the pressure side damping valve 17, and the damper D is connected to the expansion side chamber R1. Thrust is exerted by the differential pressure in the compression side chamber R2. The characteristics of the expansion / contraction speed of the damper and the thrust exerted at this time are the characteristics indicated by the line (2) in FIG.

  In the state where the suspension device S has failed as described above, the damper D functions as a passive damper and suppresses the vibration of the sprung member BO and the unsprung member W, so that fail-safe operation is reliably performed in the event of a failure. Is called.

  Thus, in the suspension device S of the present invention, not only can the damper D be actively expanded and contracted to function as an active suspension, but the pump 4 must be driven in a scene where thrust as a semi-active suspension is expected to be exhibited. Instead, it is sufficient to drive the pump 4 only when it is necessary to reduce the energy consumption. Therefore, according to the suspension device S of the present invention, it can function as an active suspension and energy consumption is reduced.

  In the suspension device S of the present invention, since the thrust of the damper D can be controlled only by the differential pressure control valve 9, the entire device is compared with a conventional suspension device that requires two electromagnetic valves. In addition to the low cost, the piping of the fluid pressure circuit can be simplified.

  Further, this suspension device S can function not only as an active suspension, but also can provide a fail-safe operation in the event of a failure only by providing one differential pressure control valve 9 equipped with a solenoid.

  In addition, the driver Dr for driving the differential pressure control valve 9 only needs to have a drive circuit for driving the solenoid Sol. Therefore, compared to a suspension device that requires two conventional solenoid valves, The number of drive circuits held by the driver Dr is small. Therefore, the cost of the driver Dr that drives the suspension device S is also reduced.

  Further, in the suspension device S of the present embodiment, the differential pressure is provided in parallel with the expansion side damping valve 15 that provides resistance to the flow from the expansion side chamber R1 toward the differential pressure control valve 9, and the expansion side damping valve 15. In parallel with the expansion side check valve 16 that allows only the flow from the control valve 9 to the expansion side chamber R1, the pressure side damping valve 17 that provides resistance to the flow from the pressure side chamber R2 to the differential pressure control valve 9, and the pressure side attenuation valve 17. And a pressure side check valve 18 that allows only the flow from the differential pressure control valve 9 toward the pressure side chamber R2. Therefore, when supplying fluid from the pump 4 to the extension side chamber R1 or the pressure side chamber R2, the fluid can be supplied to the extension side chamber R1 or the pressure side chamber R2 through the extension side check valve 16 or the pressure side check valve 18 with almost no resistance. The load on the pump 4 can be reduced when the expansion / contraction direction of the damper D coincides with the direction of thrust to be generated. Further, when the fluid is discharged from the expansion side chamber R1 or the compression side chamber R2, resistance is given to the flow of the fluid passing through the expansion side damping valve 15 or the compression side attenuation valve 17, and therefore the difference between the expansion side chamber R1 and the compression side chamber R2 A large thrust can be obtained by making the pressure equal to or greater than the differential pressure that can be set by the differential pressure control valve 9, and a large thrust can be generated in the suspension device S even if the thrust of the solenoid Sol in the differential pressure control valve 9 is reduced. Therefore, the differential pressure control valve 9 can be downsized and the cost can be further reduced. The expansion side damping valve 15 or the pressure side damping valve 17 may provide resistance to the fluid flow regardless of the fluid flow direction, and the expansion side damping valve 15 and the pressure side damping valve 17 allow bidirectional flow. If so, the extension side check valve 16 and the pressure side check valve 18 can be omitted.

  Further, in the suspension device S of this example, the differential pressure control valve 9 has the extension side supply position X, the pressure side supply position Y, and the neutral position N, and when energized, the extension side supply position X, the pressure side supply The differential pressure between A port a and B port b is controlled by taking either position Y or neutral position N. Therefore, the differential pressure between the A port a and the B port b can be controlled to a uniquely determined differential pressure, and the thrust of the damper D can be appropriately controlled.

  Finally, in the suspension device S described above, one damper 4 is driven by one pump 4, but as shown in FIGS. 8 and 9, a plurality of dampers D are connected between the pump 4 and the reservoir R. When the fluid pressure circuit FC is provided in each, the thrust of a plurality of dampers D can be generated by one pump 4. Specifically, in the suspension device S1 in the second embodiment of FIG. 8, in order to drive two dampers D for one pump 4, a shunt valve is provided between the pump 4 and each fluid pressure circuit FC. 80, and the fluid discharged from the pump 4 is distributed to each fluid pressure circuit FC by the flow dividing valve 80. The flow dividing valve 80 equally divides the discharge flow rate of the pump 4 and distributes it to the two fluid pressure circuits FC. However, it may be distributed at a different ratio.

  In the suspension device S2 in the third embodiment of FIG. 9, in order to drive the four dampers D with respect to one pump 4, three branch valves 90 are provided between the pump 4 and the four fluid pressure circuits FC. , 91, 92 are provided, and the fluid discharged from the pump 4 is distributed to the four fluid pressure circuits FC by the diversion valves 90, 91, 92. The diverter valves 90, 91, and 92 are configured to equally divide the discharge flow rate of the pump 4 and distribute it to the four fluid pressure circuits FC.

  In this way, if the discharge flow rate from the pump 4 is distributed to the fluid pressure circuit FC provided for each damper D using the diversion valves 80, 90, 91, 92, each damper D can be driven by one pump 4. It is possible to supply the flow rate necessary to generate the thrust. Therefore, only one motor is required for generating the thrust of the plurality of dampers D, and only one drive circuit for driving the motor 13 in the driver Dr is required. Therefore, the cost of the entire system can be reduced even if the number of dampers D increases. .

  This is the end of the description of the embodiments of the present invention, but the scope of the present invention is not limited to the details shown or described.

DESCRIPTION OF SYMBOLS 1 ... Cylinder, 2 ... Piston, 4 ... Pump, 5 ... Supply path, 6 ... Discharge path, 7 ... Extension side path, 8 ... Pressure side path, 9 ... Differential pressure control valve, 10 ... suction passage, 11 ... suction check valve, 12 ... supply side check valve, 15 ... extension side damping valve, 16 ... extension side check valve, 17 ..Pressure side damping valve, 18 ... Pressure side check valve, 64 ... Port (A port), 65 ... Port (B port), 66,67 ... Port (P port), 68,69 ..Port (T port), 80, 90, 91, 92... Diverging valve, a ... A port, b ... B port, D ... Damper, F ... Fail position, FC ..Fluid pressure circuit, N ... neutral position, p ... P port, R ... reservoir, R1 ... extension side chamber, 2 ... compression side chamber, S, S1, S2 ··· suspension system, t ... T ports, X ... extension side supply position, Y ... pressure side supply position

Claims (4)

A damper having a cylinder and a piston that is movably inserted into the cylinder and divides the cylinder into an extension side chamber and a pressure side chamber;
A pump,
A reservoir connected to the suction side of the pump;
A supply path connected to the discharge side of the pump;
A discharge path connected to the reservoir;
An extension passage connected to the extension chamber;
A pressure side passage connected to the pressure side chamber;
An extension side damping valve provided in the extension side passage;
A pressure side damping valve provided in the pressure side passage;
An A port connected to one of the extension side passage and the pressure side passage, a B port connected to the other of the extension side passage and the pressure side passage, a P port connected to the supply passage, and the discharge passage 4 port 4 position which has 4 ports of T port connected to the A port and controls the differential pressure between the A port and the B port when energized, and adopts a fail position where all the ports communicate with each other when deenergized A differential pressure control valve of
A supply side check valve provided between the differential pressure control valve and the pump in the middle of the supply path and allowing only a flow from the pump side to the differential pressure control valve side;
A suction passage connecting the discharge passage between the differential pressure control valve and the supply side check valve in the middle of the supply passage;
A suction check valve that is provided in the middle of the suction passage and allows only a flow of fluid from the discharge passage toward the supply passage;
A suspension device comprising: A plurality of dampers including a cylinder and a piston that is movably inserted into the cylinder and divides the cylinder into an extension side chamber and a pressure side chamber;
A pump,
A reservoir connected to the suction side of the pump;
A plurality of fluid pressure circuits provided for each of the dampers;
A flow dividing valve for distributing the fluid discharged from the pump to the fluid pressure circuits,
The fluid pressure circuit is:
A supply path connected to the discharge side of the pump via the diversion valve;
A discharge path connected to the reservoir;
An extension passage connected to the extension chamber;
A pressure side passage connected to the pressure side chamber;
An extension side damping valve provided in the extension side passage;
A pressure side damping valve provided in the pressure side passage;
An A port connected to one of the extension side passage and the pressure side passage, a B port connected to the other of the extension side passage and the pressure side passage, a P port connected to the supply passage, and the discharge passage 4 port 4 position which has 4 ports of T port connected to the A port and controls the differential pressure between the A port and the B port when energized, and adopts a fail position where all the ports communicate with each other when deenergized A differential pressure control valve of
A supply side check valve provided between the differential pressure control valve and the pump in the middle of the supply path and allowing only a flow from the pump side to the differential pressure control valve side;
A suction passage connecting the discharge passage between the differential pressure control valve and the supply side check valve in the middle of the supply passage;
A suspension check valve provided in the middle of the suction passage and allowing only a flow of fluid from the discharge passage toward the supply passage. An extension side check valve that is provided in parallel to the extension side damping valve in the extension side passage and allows only a flow from the differential pressure control valve toward the extension side chamber;
The pressure-side check valve is provided in parallel to the pressure-side damping valve in the pressure-side passage and allows only a flow from the differential pressure control valve toward the pressure-side chamber. Suspension device. The differential pressure control valve communicates the A port with the P port and communicates the B port with the T port, a neutral supply position with which all the ports communicate with each other, and the A port. And a pressure side supply position that communicates the B port and the P port, and takes one of the extension side supply position, the neutral position, or the pressure side supply position when energized. The suspension device according to any one of claims 1 to 3, wherein

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