JP2007296936A - Vibration suppression device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a compact vibration suppression device having functions of semi-active and full-active ones. <P>SOLUTION: The vibration suppression device 1 has a cylinder 2 for suppressing the vibration interposed between a carriage and a vehicle body, a reservoir tank 3 connected to a head side chamber 13 of the cylinder 2 for suppressing the vibration via a check valve 16, a rod side flow passage 24 connected to a rod side chamber 14 of the cylinder 2 for suppressing the vibration, a head side flow passage 22 connected to the head side chamber 13 of the cylinder 2 for suppressing the vibration, and a reservoir side flow passage 23 connected to the reservoir tank 3. Furthermore, the vibration suppression device has a change valve 4 for controlling communication/shutoff of the head side flow passage 22 with the rod side flow passage 24, and the head side flow passage 23 with the reservoir side flow passage 23, a relief valve 5 provided in the flow passage 25 for connecting the rod side flow passage 24 and the reservoir tank 3, and an accumulator 6 connected to the rod side flow passage 24. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a vibration suppressing device for suppressing the shaking of a vehicle body that occurs during traveling of a railway vehicle and improving riding comfort, and in particular, a compact that can be used as both a semi-active device and a full-active device. The present invention relates to a vibration suppression device.

  In railway vehicles, an air spring is generally provided between the bogie and the car body to reduce the vibration from the bogie and improve the ride comfort, but the air spring cannot attenuate the vibration, so the vibration continues. There is a problem of resonance with disturbance. Therefore, a vibration suppressing device (damper) is provided between the carriage and the vehicle body in order to attenuate the lateral vibration of the air spring. Various types of vibration suppression devices are used, but a so-called semi-active damper is known in which the degree of vibration suppression can be changed depending on the degree of lateral vibration. For example, Japanese Patent Laid-Open No. 9-301164 It is described in. The configuration of this semi-active damper will be described with reference to FIG.

  The vibration suppressing device 100 is configured by a hydraulic circuit that connects the rod side chamber 111, the head side chamber 112, and the reservoir tank 120 of the hydraulic cylinder 110. In the hydraulic cylinder 110, for example, the end of the piston rod 113 is fixed to the carriage, and the cylinder head 114 is fixed to the vehicle body. The head side chamber 112 and the rod side chamber 111 of the hydraulic cylinder 110 are separated by a piston 115 in which a check valve 116 is formed. The head side chamber 112 is connected to the reservoir tank 120 via a check valve 121, and the rod side chamber 111 flows from the flow path 200 via orifices 131, 132, 133, 134 and high-speed solenoid valves 141, 142, 143, 144. The passage 300 is connected to the reservoir tank 120.

In the vibration suppression device 100, when the piston rod 113 contracts, the hydraulic oil in the head side chamber 112 flows into the rod side chamber 111 through the check valve 116 and is pushed out to the flow path 200. Further, when the piston rod 113 is extended, the hydraulic oil in the rod side chamber 111 is discharged to the flow path 200, and the hydraulic oil is sucked from the reservoir tank 120 through the check valve 121 into the head side chamber 112 having a negative pressure.
The hydraulic oil pushed out to the flow path 200 passes through the orifices 131 to 133 by ON / OFF of the high-speed electromagnetic valves 141 to 143 at the time of on-road, and a damping force is generated due to the orifice throttling effect. In addition, when unloading, the hydraulic oil flows into the flow path 300 through the high-speed solenoid valves 134 and 144 and no damping force is generated, and when not energized, the hydraulic oil returns to the flow path 300 through the orifice 134. Then it becomes a fail state.
JP-A-9-301164 (page 7-8, FIG. 7) JP 2002-126965 A (5th page, FIG. 3, FIG. 4)

However, such a conventional vibration suppression device 100 has a multi-stage damping force in order to finely apply the damping force corresponding to various vibration states of the vehicle body, and has a high-speed solenoid valve and a hydraulic circuit configuration. It has become complicated.
Further, the vibration suppressing device 100 is a semi-active damper and is unloaded at about half the timing, so that the vibration damping effect is not sufficient. For example, when the vehicle body shakes due to an aerodynamic disturbance when passing with an oncoming vehicle, and the vehicle rolls, it is often seen that the vehicle body and the carriage swing left and right in the same phase. In such a case, there is a problem that the semi-active damper has a low on-road timing, and even when on-road, the damper speed is too small to exhibit a sufficient control effect. Therefore, development of a vibration suppressing device in which a full-acting function is added to the semi-acting function is desired, but the size is increased, and for example, it is not practical as a device mounted on a railway vehicle.

  By the way, the vibration suppressing device needs to be able to completely follow the required relative displacement between the vehicle body and the carriage. However, as a configuration for that purpose, since a pump, a motor, and an accumulator have become very large in the past, they cannot be integrated, and pipes and hoses for connecting each device are required. Then, the apparatus connected by piping was difficult to handle, and there was a problem that maintenance and the like were inconvenient, which was not practical. Further, when the piston speed cannot be followed completely, the vibration insulation between the vehicle body and the carriage is lost, and there is a problem that the ride comfort is deteriorated.

  Accordingly, an object of the present invention is to provide a compact vibration suppression device having functions of semi-active and full-active in order to solve such problems.

  The vibration suppression device according to the present invention includes a vibration suppression cylinder interposed between a carriage and a vehicle body, a reservoir tank connected to a head side chamber of the vibration suppression cylinder via a check valve, and the vibration suppression cylinder. A rod-side channel connected to the rod-side chamber of the cylinder; a head-side channel connected to the head-side chamber of the vibration suppressing cylinder; a reservoir-side channel connected to the reservoir tank; and the head-side channel. A switching valve for controlling communication / blocking between the rod side flow path, the head side flow path and the reservoir side flow path, and a relief valve provided in a flow path connecting the rod side flow path and the reservoir tank; And an accumulator connected to the rod side flow path.

Further, in the vibration suppressing device according to the present invention, the switching valve switches the connection between the head side flow path and the rod side flow path and the connection between the head side flow path and the reservoir side flow path. It is preferable that
Further, in the vibration suppressing device according to the present invention, the switching valve is a three-way proportional control valve capable of adjusting an opening degree, and the relief valve is an electromagnetic proportional relief valve capable of changing a relief pressure setting. It is preferable to have a controller that controls the three-way proportional control valve and the electromagnetic proportional relief valve.

In the vibration suppressing device according to the present invention, it is preferable that a pump is provided in a flow path connecting the rod side flow path and the reservoir tank.
Further, in the vibration suppressing device according to the present invention, the switching valve is a three-way proportional control valve capable of adjusting an opening degree, and the relief valve is an electromagnetic proportional relief valve capable of changing a relief pressure setting, The pump is preferably a motor pump, and preferably has a controller for controlling the three-way proportional control valve, the electromagnetic proportional relief valve, and the motor pump.

  Therefore, according to the vibration suppression device of the present invention, when the pump is driven, the accumulator is accumulated and can function as a complete full active damper, even when the pump does not drive or does not have a pump. By experiencing on-road control, the accumulator is accumulated and functions as an accumulator active damper. Furthermore, even when the accumulator pressure accumulation function is not functioning, it can function as a conventional semi-active damper and can be passively controlled. It is configured as a device.

Next, an embodiment of a vibration suppressing device according to the present invention will be described below with reference to the drawings. FIG. 1 is a circuit diagram showing an embodiment of a vibration suppressing device.
In the vibration suppression device 1, a vibration suppression cylinder 2 is connected between the carriage and the vehicle body to prevent the vehicle body from shaking. In the vibration suppressing cylinder 2, a piston rod 12 is fixed to a piston 11 slidable in an airtight manner, and the piston rod 12 protrudes in an axial direction. The piston 11 is formed with a check valve 15 that allows only the flow of hydraulic oil from the head side chamber 13 toward the rod side chamber 14. The head side chamber 13 and the rod chamber 14 separated by the piston 11 are filled with the working fluid together with the connected flow path.

  The head side chamber 13 and the rod side chamber 14 of the vibration suppressing cylinder 2 are connected to the reservoir tank 3. The head side chamber 13 is connected via a flow path 21 provided with a check valve 16 so that the flow from the head side chamber 13 to the reservoir tank 3 is blocked. Further, the head side chamber 13 is connected to the head side flow path 22 and is connected from the reservoir side flow path 23 to the reservoir tank 3 via the three-way proportional control valve 4. On the other hand, the rod side flow path 24 is connected to the rod side chamber 14, and the rod side flow path 24 is connected to the three-way proportional control valve 4. Then, a connecting flow path 25 provided with the electromagnetic proportional relief valve 5 is branched to the rod side flow path 24 and connected to the reservoir tank 3.

  The three-way proportional control valve 4 of the present embodiment includes an A port pattern that connects the head side flow path 22 and the reservoir side flow path 23, and a B port pattern that connects the head side flow path 22 and the rod side flow path 24. Is switched. When the solenoid is energized (ON control), the A port pattern is connected, and when OFF, the B port pattern is connected. Therefore, normally, the head side flow path 22 and the rod side flow path 24 are connected, and the head side chamber 13 and the rod side chamber 14 are in communication with each other. The three-way proportional control valve 4 is configured to be manually operable, and can be manually switched from the normal state of the B port pattern to the A port pattern.

Next, the electromagnetic proportional relief valve 5 provided in the connection flow path 25 is for generating a damping force in the vibration suppressing cylinder 2 by controlling the resistance when hydraulic fluid passes through. The electromagnetic proportional relief valve 5 and the three-way proportional control valve 4 are solenoid valves, and a port is switched and a relief pressure is set by a control signal from the controller 7. The proportional relief pressure is controlled to be a value obtained by multiplying an absolute speed obtained by integrating the lateral acceleration of the vehicle body by a proportional gain. The three-way proportional control valve 4 is switched ON / OFF according to the sign of the absolute speed obtained by integrating the vehicle body lateral acceleration.
Furthermore, an accumulator 6 is connected to the rod side flow path 24 in the vibration suppressing device 1. In this embodiment, for example, the accumulator 6 is set at a gas pressure of 4 MPa, and the electromagnetic proportional relief valve 5 is set so that the maximum relief pressure is 8 MPa.

  The vibration suppression device 1 of the present embodiment is for attenuating the lateral vibration of an air spring in a railway vehicle, and a vibration suppression cylinder 2 is connected between the carriage and the vehicle body. For example, the piston rod 12 of the vibration suppressing cylinder 2 is connected to the carriage, and the cylinder head is connected to the vehicle body (or may be attached in the opposite direction). The vehicle is provided with an acceleration sensor (not shown) that detects acceleration accompanying rolling of the vehicle body, and the controller 7 performs switching control of the three-way proportional control valve 4 based on the acceleration signal.

Therefore, the vibration suppression device 1 determines whether or not to generate a damping force in the vibration suppression cylinder 2, that is, on-load or unload is determined, and the three-way proportional control valve 4 is switched according to the determination. In addition, the vibration suppression device 1 of the present embodiment includes the accumulator 6 so that the vibration suppression cylinder 2 functions as a semi-active damper and also functions as an active damper as follows.
First, a description will be given of a state where the accumulator does not function, that is, a case where the vibration suppressing device 1 functions as a semi-active damper when a pressure higher than a set pressure is applied to the working fluid or a state where accumulated pressure is released. 2 to 5 are diagrams illustrating the flow of hydraulic oil when functioning as a semi-active damper. Here, the accumulator 6 is omitted. A thick wavy line indicates the flow of the high-pressure fluid that causes the damping cylinder 2 to generate a damping force, and a thin wavy line indicates the flow of the low-pressure fluid that occurs in accordance with the flow of the high-pressure fluid.

  When on-load control is performed on the expansion of the vibration suppressing cylinder 2, an ON signal is transmitted from the controller 7, and the three-way proportional control valve 4 is switched to the connection of the A port pattern as shown in FIG. . As a result, the head-side flow path 22 and the rod-side flow path 24 are blocked by the three-way proportional control valve 4. Therefore, the hydraulic oil that has been pulled out of the piston-side chamber 14 and pushed out of the rod-side chamber 14 flows through the rod-side flow path 24 and is sent to the reservoir tank 3 through the electromagnetic proportional relief valve 5. Thus, the hydraulic oil in the circuit flows through the electromagnetic proportional relief valve 5 having a passive relief pressure characteristic, so that a damping force is generated in the vibration suppressing cylinder 2. On the other hand, since the head side chamber 13 becomes negative pressure due to the extension of the vibration suppressing cylinder 2, it flows from the reservoir tank 3 through the flow path 21, the reservoir side flow path 23, and the head side flow path 22.

  Next, when on-load control is performed for the contraction of the vibration suppressing cylinder 2, an OFF signal is transmitted from the controller 7, and the three-way proportional control valve 4 is connected to the B port pattern as shown in FIG. Can be switched to. As a result, the rod-side flow path 24 and the head-side flow path 22 communicate with each other via the three-way proportional control valve 4. Therefore, the hydraulic oil pushed out from the head side chamber 13 by the piston rod 12 being pushed in is pushed out to the head side flow path 22 and flows into the rod side flow path 24, and a part of the hydraulic oil flows through the check valve 15. It is sent to the side chamber 14 and also flows from the rod side chamber 14 to the rod side flow path 24. The hydraulic oil pushed out from the vibration suppressing cylinder 2 is sent from the connection flow path 25 to the reservoir tank 3. At this time, since the hydraulic oil flows through the electromagnetic proportional relief valve 5 having a passive characteristic of the relief pressure, a damping force is generated in the vibration suppressing cylinder 2.

  On the other hand, when the unload control is performed on the expansion of the vibration suppressing cylinder 2, an OFF signal is transmitted from the controller 7, and the three-way proportional control valve 4 is connected to the B port pattern as shown in FIG. Can be switched. As a result, the rod-side flow path 24 and the head-side flow path 22 communicate with each other via the three-way proportional control valve 4. Therefore, when the piston rod 12 is pulled out, the hydraulic oil pushed out from the rod side chamber 14 flows into the rod side flow path 24. Then, the hydraulic oil flows through the three-way proportional control valve 4 and flows back to the head side chamber 13 from the head side flow path 22 where the negative pressure is obtained. Further, since the head side flow path 22 has a negative pressure, the hydraulic oil is also sent from the reservoir tank 3 through the flow path 21. Accordingly, at this time, no damping force is generated in the vibration suppressing cylinder 2.

  Next, when the unload control is performed for the contraction of the vibration suppressing cylinder 2, an ON signal is transmitted from the controller 7, and the three-way proportional control valve 4 is connected to the A port pattern as shown in FIG. Can be switched to. As a result, the head-side flow path 22 is connected to the reservoir-side flow path 23 via the three-way proportional control valve 4. Therefore, the hydraulic oil pushed out from the head side chamber 13 by the piston rod 12 being pushed in is pushed out to the head side flow path 22 and sent from the reservoir side flow path 23 to the reservoir tank 3 through the three-way proportional control valve 4. . The hydraulic oil in the head side chamber 13 also flows to the rod side chamber 14 where a part passes through the check valve 15 of the piston 15 and becomes negative pressure. Accordingly, in this case, no damping force is generated in the vibration suppressing cylinder 2.

  Next, the case where the vibration suppression apparatus 1 functions as an active damper when the accumulator 6 functions will be described. 6 to 9 are diagrams illustrating the flow of hydraulic oil when functioning as an active damper. A thick wavy line indicates the flow of the high-pressure fluid that causes the vibration suppressing cylinder 2 to generate a damping force or an operating pressure, and a thin wavy line indicates the flow of the low-pressure fluid generated according to the flow of the high-pressure fluid.

  When on-load control is performed on the expansion of the vibration suppressing cylinder 2, an ON signal is transmitted from the controller 7, and the three-way proportional control valve 4 is switched to the connection of the A port pattern as shown in FIG. . Therefore, when the piston rod 12 is pulled out and the hydraulic oil in the rod side chamber 14 is pressurized, the hydraulic oil in the rod side chamber 14 is pushed out to the rod side flow path 24. Since the head-side flow path 22 is blocked by the three-way proportional control valve 4, the pressure in the rod-side flow path 24 increases, and the set pressure is attenuated to the vibration suppression cylinder 2 by the accumulator 6. Force is generated. Further, when the pressure in the rod side flow path 24 exceeds the relief pressure, the electromagnetic proportional relief valve 5 is opened and the hydraulic oil flows to the reservoir 3 as shown in FIG. Will occur. Then, hydraulic oil is fed from the reservoir tank 3 through the flow path 21, the reservoir-side flow path 23, and the head-side flow path 22 into the head side chamber 13 that has become negative pressure.

  Next, when on-load control is performed for the contraction of the vibration suppression cylinder 2, an OFF signal is transmitted from the controller 7, and the three-way proportional control valve 4 is connected to the B port pattern as shown in FIG. Can be switched to. Therefore, when the piston rod 12 is pushed in and the hydraulic oil in the head side chamber 13 is pressurized, the hydraulic oil in the head side chamber 13 is pushed out to the head side flow path 22 and flows to the rod side flow path 24. Further, a part is sent from the check valve 15 of the piston 15 to the rod side chamber 14, and also flows from the rod side chamber 14 to the rod side flow path 24. And the pressure in the rod side flow path 24 becomes high, and a damping force is generated in the vibration suppressing cylinder 2 by the pressure accumulation action by the accumulator 6 up to the set pressure. Further, when the pressure in the rod side flow path 24 exceeds the relief pressure, the electromagnetic proportional relief valve 5 opens and the hydraulic oil flows to the reservoir 3 as shown in FIG. appear.

Subsequently, when active unload control is performed for the extension of the vibration suppressing cylinder 2, an OFF signal is transmitted from the controller 7, and the three-way proportional control valve 4 is connected to the B port pattern as shown in FIG. Can be switched to. As a result, the rod side flow path 24 and the head side flow path 22 communicate with each other via the three-way proportional control valve 4, and the accumulator 6 is connected to the cylinder side chamber 13 and the rod side chamber 14 of the vibration suppression cylinder 2. Therefore, pressure is released from the accumulator 6 in the pressure accumulation state by the flow of hydraulic oil.
In the cylinder 2 for vibration suppression, the cylinder side chamber 13 has a larger hydraulic pressure receiving area than the rod side chamber 14 by the cross-sectional integral of the piston rod 12. Therefore, when pressurized from both sides, the piston 11 slides in the direction in which the pressure on the cylinder side chamber 13 side increases and the piston rod 12 extends. As a result, the vibration suppressing cylinder 2 is extended, the hydraulic oil in the rod side chamber 14 is pushed out, the hydraulic oil pushed out from the rod side chamber 14 is refluxed, and the hydraulic oil is sent into the head side chamber 13.

  On the other hand, when active unload control is performed for the contraction of the vibration suppressing cylinder 2, an ON signal is transmitted from the controller 7, and the three-way proportional control valve 4 is connected to the A port pattern as shown in FIG. Can be switched to. Accordingly, the accumulator 6 is disconnected from the head side flow path 22 by the three-way proportional control valve 4 and is connected only to the rod side chamber 14 with respect to the vibration suppressing cylinder 2. Therefore, the pressure is released from the accumulator 6 in the pressure accumulation state by the flow of the hydraulic oil, the pressure acts on the piston 11 from the rod side chamber 14, and the piston rod 12 slides in the contracting direction. As a result, the vibration suppressing cylinder 2 contracts, the hydraulic oil in the head side chamber 13 is pushed out to the head side flow path 22 and flows from the reservoir side flow path 23 to the reservoir tank 3 through the three-way proportional control valve 4.

  By the way, the vibration suppression apparatus 1 can function as an active damper using the pressure of the accumulator 6. However, this is a function that is enabled when the accumulator 6 is accumulated during on-load control. Therefore, next, a complete active damper is proposed in which a pump is added to the vibration suppression device 1 so that the accumulator 6 can always accumulate pressure. FIG. 10 is a circuit diagram showing the vibration suppressing device 10 functioning as a full active damper. In addition, it is the same as the vibration suppression apparatus 1 shown in FIG. 1 except the added structure.

The motor pump 8 is provided on a flow path 26 that connects the reservoir tank 3 and the rod side flow path 24, and can supply hydraulic oil of the reservoir tank 3 from the rod side flow path 24 to the accumulator 6. Further, a check valve 17 is provided in the flow path 26 and is blocked so that the high-pressure fluid in the rod side flow path 24 does not flow into the reservoir tank 3. The motor pump 8 is connected to the controller 7, and drive control is performed by a control signal.
Therefore, when the accumulator 6 releases pressure and cannot perform active control, an ON signal is transmitted from the controller 7 and the three-way proportional control valve 4 is switched to the connection of the A port pattern as shown. Then, a drive signal is further transmitted from the controller 7 to the motor pump 8, and the hydraulic oil in the reservoir tank 3 is sent out to the rod side flow path 24.

  Thereby, the pressure is increased by the hydraulic oil sent to the rod-side flow path 24, and the accumulator 6 is accumulated to the set pressure. And the controller 7 receives the detection signal from the pressure sensor not shown provided in the rod side flow path 24, and stops the motor pump 8. FIG. Therefore, the vibration suppression device 10 can always create a state in which the accumulator 6 accumulates pressure, and as described with reference to FIGS. 8 and 9, the full active damper that can always expand and contract the vibration suppression cylinder 2. Function as.

  When the motor pump 8 is driven, the vibration suppressing device 10 of the present embodiment accumulates the accumulator 6 and can function as a complete full active damper. Further, even when the motor pump 8 is not driven, or even in the vibration suppression device 1 shown in FIG. 1, the accumulator 6 is accumulated by experiencing on-road control, and functions as a pressure accumulation type active damper. Further, the vibration suppression devices 1 and 10 function as a conventional semi-active damper and can be passively controlled even when the accumulator 6 has no pressure accumulation function. Therefore, according to the vibration suppression devices 1 and 10 of the present embodiment, a single unit has the functions of semi-active and full-active, and as can be seen from FIGS. 1 and 10, the number of parts is small, and the configuration is simple and compact. It is. When the vehicle body is forcibly displaced left and right by full active control, the small accumulator 6 and motor pump 8 operate slowly. However, it is still effective, for example, for avoiding or avoiding impact per stopper when passing the curve toward the inside of the curve, or for bringing the vehicle body to the home and exhibiting a barrier-free effect when the vehicle stops.

Further, according to the vibration suppression device 1 of the present embodiment, in the case as shown in FIGS. 8 and 9, the accumulated pressure of the accumulator 6 is used to exert power at the initial stage even during unloading. As a result, the duration of the vibration control effect can be extended compared to conventional semi-active dampers.
Further, the motor pump 8 constituting the vibration suppressing device 10 may be small because it can accumulate the accumulator 6. Therefore, it is easy to integrate the motor pump 8 with respect to the vibration suppressing device 1 shown in FIG. 1, and the performance can be improved as compared with the vibration suppressing device 1 by including the motor pump 8.

In addition, the conventional vibration suppression device may be attached to the vehicle body without using a jig because pressure is applied to the hydraulic fluid in the flow path and the vibration suppression cylinder is extended. However, in the vibration suppression devices 1 and 10 of the present embodiment, since the three-way proportional control valve 4 can be manually switched, vibration is generated by releasing the pressure by connecting the head side flow path 22 to the reservoir tank 3. The restraining cylinder 2 can be shortened, and handling becomes extremely easy.
Further, since the vibration suppression devices 1 and 10 are provided with the accumulator 6, the hydraulic oil in the flow path is pressurized by the accumulated pressure, so that no negative pressure is generated and bubbles are not generated in the pipe. Therefore, it is possible to always maintain high performance with respect to the vibration suppressing effect.

  By the way, in the vibration suppression apparatus 10, the relief pressure of the electromagnetic proportional relief valve 5 may be set to a value lower than the pressure accumulation limit of the accumulator 6, and the motor pump 8 may be always driven after the control is started. In this case, the pressure sensor is unnecessary, and the hydraulic oil is returned to the reservoir tank 3 and circulated, which is also safe. As the vibration suppression device 10, a small motor pump 8 is used and the discharge amount is extremely small. However, even a small force can be sufficiently suppressed by a vibration suppression operation before the kinetic energy increases. Excellent effect. Such a small vibration suppression device 10 naturally functions as a semi-active damper from the full active damper when the discharge amount of the motor pump 8 is insufficient or when the accumulator 6 has accumulated pressure.

Next, another embodiment of the vibration suppressing device according to the present invention will be briefly described. The vibration suppressing device of each embodiment is configured to be able to achieve a fail-safe effect at the time of failure. In addition, the vibration suppression apparatus shown below attaches | subjects and demonstrates the same code | symbol about the same structure as the vibration suppression apparatus 1 shown in FIG.
The vibration suppressing device 30 shown in FIG. 11 has a three-port three-block three-way valve 31 connected between flow paths 22, 23, and 24. Therefore, in the normal state, as shown in the figure, the flow paths 22, 23, 24 are blocked, so when the vibration suppressing cylinder 2 expands and contracts, hydraulic oil is discharged only from the rod side chamber 14, and the electromagnetic proportional relief valve 5 is opened. Since it flows through, it functions as a passive damper. Similarly, instead of the three-way valve 31, a four-port three-block three-way valve may be used.

  Further, in the vibration suppressing device 40 shown in FIG. 12, an ON / OFF valve 41 is connected between the flow paths 22 and 23, and an ON / OFF valve 42 is connected between the flow paths 22 and 23 in the same manner. Is. Therefore, in the normal state, as shown in the figure, the flow paths 22 and 23 and the flow paths 22 and 24 are blocked, so that the hydraulic oil is discharged only from the rod side chamber 14 when the vibration suppressing cylinder 2 expands and contracts. Since it flows through the electromagnetic proportional relief valve 5, it functions as a passive damper. The ON / OFF valves 41 and 42 are switched to the communication side by a push button.

  Further, in the vibration suppressing device 50 shown in FIG. 13, an ON / OFF valve 51 is connected to the rod side flow path 24, and the accumulator 6, the motor pump 8, and the like are connected between the ON / OFF valve 51 and the three-way proportional control valve 4. A check valve 17 is connected. The ON / OFF valve 51 is energized simultaneously with the start of control. Therefore, in the normal state, as shown in the figure, the flow path 22, 23 is blocked by the three-way proportional control valve 4, and the flow path 22, 24 is blocked by the ON / OFF valve 51, so that the vibration suppressing cylinder 2 expands and contracts. In this case, the hydraulic oil is discharged only from the rod side chamber 14 and flows through the electromagnetic proportional relief valve 5 so that it functions as a passive damper. Note that the motor pump 8 stops driving during a failure.

  As mentioned above, although one Embodiment of the vibration suppression apparatus which concerns on this invention was described, this invention is not limited to this, A various change is possible in the range which does not deviate from the meaning.

It is the circuit diagram which showed one Embodiment of the vibration suppression apparatus. It is a circuit diagram of a vibration suppression device functioning as a semi-act, showing the flow of hydraulic oil during elongation on-road control. It is a circuit diagram of a vibration suppression device functioning as a semi-act, showing the flow of hydraulic oil during shrink on-road control. It is a circuit diagram of a vibration suppression device functioning as a semi-act, showing a flow of hydraulic oil during elongation unload control. It is a circuit diagram of a vibration suppression device functioning as a semi-act, showing the flow of hydraulic oil during shrinkage unloading control. FIG. 3 is a circuit diagram of a vibration suppressing device functioning as a full operation showing a flow of hydraulic oil during elongation on-road control. FIG. 3 is a circuit diagram of a vibration suppressing device functioning as a full operation showing a flow of hydraulic oil during shrink on-road control. FIG. 3 is a circuit diagram of a vibration suppressing device functioning as a full operation showing a flow of hydraulic oil during elongation unload control. FIG. 3 is a circuit diagram of a vibration suppressing device functioning as a full operation showing a flow of hydraulic oil during shrinkage unloading control. It is the circuit diagram which showed embodiment of the vibration suppression apparatus provided with the pump. It is the circuit diagram which showed embodiment of the vibration suppression apparatus which uses the 3 way valve of 3 port 3 block. It is the circuit diagram which showed embodiment of the vibration suppression apparatus which uses an ON / OFF valve. It is the circuit diagram which showed other embodiment of the vibration suppression apparatus provided with the pump. It is the circuit diagram which showed the conventional semi-active damper.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1,10 Vibration suppression device 2 Vibration suppression cylinder 3 Reservoir tank 4 Three-way proportional control valve 5 Electromagnetic proportional relief valve 6 Accumulator 7 Controller 8 Motor pump 11 Piston 12 Piston rod 13 Head side chamber 14 Rod chamber 15 Check valve 16 Check valve 21 Flow Path 22 head side channel 23 reservoir side channel 24 rod side channel 25 connection channel

Claims (5)

  A vibration suppression cylinder interposed between the carriage and the vehicle body, a reservoir tank connected to the head side chamber of the vibration suppression cylinder via a check valve, and a rod connected to the rod side chamber of the vibration suppression cylinder A side channel, a head side channel connected to the head side chamber of the vibration suppressing cylinder, a reservoir side channel connected to the reservoir tank, the head side channel, the rod side channel, and the head side A switching valve that controls communication / blocking between the flow path and the reservoir side flow path, a relief valve provided in a flow path that connects the rod side flow path and the reservoir tank, and a connection to the rod side flow path. A vibration suppression device characterized by comprising an accumulator. In the vibration suppression device according to claim 1,
The switching valve is a three-way valve that switches a connection between the head-side flow path and the rod-side flow path and a connection between the head-side flow path and the reservoir-side flow path. In the vibration suppressing device according to claim 1 or 2,
The switching valve is a three-way proportional control valve whose opening degree can be adjusted, and the relief valve is an electromagnetic proportional relief valve whose relief pressure can be changed. The three-way proportional control valve and the electromagnetic proportional relief valve are controlled. A vibration suppression device comprising a controller that performs the above-described operation. In the vibration suppression device according to any one of claims 1 to 3,
A vibration suppression apparatus, wherein a pump is provided in a flow path connecting the rod side flow path and the reservoir tank. In the vibration suppression device according to claim 4,
The switching valve is a three-way proportional control valve capable of adjusting the opening degree, the relief valve is an electromagnetic proportional relief valve capable of changing a relief pressure setting, and the pump is a motor pump, and this three-way proportional A vibration suppressing device comprising a controller for controlling a control valve, an electromagnetic proportional relief valve, and a motor pump.

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