JP2002114144A - Damper for vibration suppression - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a damper for vibration suppression that is compact. SOLUTION: The damper 1 for vibration suppression has a cylinder 10 wherein a head-side chamber 13 and a rod-side chamber 14 intercommunicate via a passage formed in a piston 12 and provided with a check valve 15; a damping circuit wherein the head-side chamber 13 and an oil tank 20 are connected via a check valve 19, the rod-side chamber 14 and the oil tank 20 are connected via a passage with two passages forming a loading state and an unloading state, and the loading and unloading passages are changed over by a mechanical control valve 25; and an operating circuit wherein operating valves 27 and 28 operate pressure transmission in the head-side chamber 13 by extending and retracting motion of the cylinder 10 to thus control operating pressure on the mechanical control valve 26.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a vibration damper for suppressing vibration of a vehicle body during traveling of a railway vehicle and improving ride comfort, and more particularly to a vibration damper that is made compact.

[0002]

2. Description of the Related Art In a railway vehicle, an air spring provided between a bogie and a vehicle body reduces vibration from the bogie. However, since there is no ability to attenuate the vibration of the spring by itself, an air chamber is provided. By appropriately restricting the throttle of the valve with a solenoid valve,
It is designed to serve as a damper. However, since the air spring has an extremely large response delay due to the compressibility of the air, the effect of suppressing the vibration due to the sharp reduction of the throttle area is small. There is a problem that the back is generated and the vibration is increased on the contrary.

For this reason, recently, a so-called semi-active damper has been used in which a damper for generating a damping force by the flow resistance of oil is used, and the degree of vibration damping can be varied depending on the degree of vibration. As for such a semi-active damper, various types have been proposed in which a plurality of high-speed solenoid valves are used and the damping force can be selected by switching the flow of the working fluid to respective flow paths having different throttle diameters.

[0004]

However, the conventional damper disclosed in, for example, Japanese Patent Application Laid-Open No. 8-99634 has to detect the expansion / contraction state of the damper in order to perform skyhook control. It was necessary to attach a sensor, and since it was attached to the stroke part, it was difficult to make the cylinder part compact. Further, the high-speed electromagnetic valve is determined based on control information based on control logic each time the high-speed electromagnetic valve is opened / closed based on the expansion / contraction information taken from the sensor, and the response delay of the switching is reduced. The necessity of the controller increases in size, and there is a limit to simplifying the control law and the control device.

In the case of Japanese Unexamined Patent Application Publication No. 8-99634, an unload circuit is separately provided in addition to an attenuation circuit having an orifice for generating attenuation, and the HSSH method (stretched Hard) which is in a single-effect state by this.・ Shrink S
The state of “soft” and the state of “elongation Soft / shrinkage Hard” are arbitrarily switched. However, in such an unload circuit, a pipe or an unload valve having a sufficient diameter that does not increase the flow resistance has to be used, and there is also a problem of an increase in size in this respect.

Accordingly, an object of the present invention is to provide a compact vibration damper.

[0007]

SUMMARY OF THE INVENTION Accordingly, a vibration suppressing damper according to the present invention comprises: a cylinder in which a head side chamber and a rod side chamber communicate with each other through a flow path provided with a check valve formed in a piston; The tank is connected via a check valve, and the rod-side chamber and the oil tank are connected by a flow path having two paths forming on-load and unload, and a flow forming the on-load and unload. A damping circuit capable of switching between a path and a mechanical control valve, and an operating circuit that controls the pressure transmitted to the mechanical control valve by operating the pressure transmission in the head-side chamber due to the expansion and contraction of the cylinder by the operating valve. And

Therefore, according to such a vibration suppressing damper, the opening and closing of the mechanical control valve is controlled based on the pressure information in the head-side chamber according to the operating valve, whereby the expansion or contraction of the cylinder rod is uniquely controlled. On-load or unload is determined. Accordingly, a stroke sensor for the damper and a sensor separately configured to obtain expansion / contraction information are not required, and the vibration suppression damper can be made compact.

Further, in the vibration damper of the present invention, the damping circuit has an electromagnetic variable relief valve on the on-load flow path for adjusting the fluid pressure of the working fluid by controlling the input current to the solenoid. It is characterized by. Therefore, according to the vibration suppressing damper, the pressure (damper force) of the working fluid passing through the unload can be adjusted according to the flow rate by controlling the input current to the solenoid.

Further, in the vibration damper according to the present invention, the damping circuit has a passive orifice flow path communicating the head side chamber and the oil tank at the time of a failure, and the passive orifice flow path and the on-road And a fail-safe valve for switching between a flow path and a flow path constituting two paths of unloading. Therefore, according to this vibration suppression damper, in the event of a failure such as a power failure, the damping circuit switches the sail-safe valve to communicate with the passive orifice flow path, thereby appropriately damping this vibration suppression damper. It can function as a passive damper having a coefficient.

Further, in the vibration damper of the present invention, the operating circuit may include an electromagnetic on-off valve connected to the head side chamber and a pilot line of the mechanical control valve; An operation check valve for controlling the flow to the side, and an electromagnetic three-way valve connected to the head-side chamber, the check valve, and the unloading side. Therefore, according to this vibration suppressing damper, an electromagnetic on-off valve and an electromagnetic three-way valve are used as the operating valve, and the ON / OF
The combination of F enables four patterns of attenuation control. Since the mechanical control valve can control a large flow rate with a small flow rate, a small one can be used for the operation valve and the flow path can be narrowed, so that the vibration suppressing damper can be made compact.

Further, in the vibration damper according to the present invention, the operating circuit may include an operating check valve configured to control a flow of the mechanical control valve from a pilot line to the unloading side, the head-side chamber and the mechanical control valve. And a pilot port of the check valve connected to the oil tank and an electromagnetic four-way valve for connecting the head side chamber and the pilot port of the check valve by switching. Therefore, according to the vibration suppressing damper, the configuration is further simplified by using one four-way valve as the operating valve, and the whole can be made compact.

Further, in the method of handling a vibration suppressing damper according to the present invention, a cylinder in which a head side chamber and a rod side chamber communicate with each other through a flow path having a check valve formed in a piston, and the head side chamber and an oil tank are provided. The rod side chamber and the oil tank are connected via a check valve, and the rod side chamber and the oil tank are connected by a flow path having two paths forming an on-load and an unload, and a flow path forming the on-load and the unload is formed. A damping circuit switchable by a mechanical control valve; an electromagnetic on-off valve connected to the head side chamber and a pilot line of the mechanical control valve; and an operation for controlling a flow from the pilot line of the mechanical control valve to the unload side. A check valve, an electromagnetic three-way valve connected to the head-side chamber, the check valve, and the unloading side. A damper for suppressing vibration having an operating circuit which performs two vibration suppressing dampers is mounted in one vehicle so that the ON / OFF states of the electromagnetic on-off valve and the electromagnetic three-way valve are reversed. A method of handling a damper for suppressing vibration.

Therefore, according to the method of handling the vibration suppressing damper, when one of the vibration suppressing dampers fails, the other can be backed up. At the time of a failure, one is turned on and the other is unloaded when the power is turned off. Therefore, if the damping coefficient of the on-load of one vibration suppression damper is made equal to the sum of the damping coefficients of the passive circuits provided for the failure of the two vibration suppression dampers, the on-road damping due to the failure is reduced. Even if it does, the ride comfort will not be impaired, but rather the fail-safe structure can be omitted, which greatly simplifies the structure, thereby making it lighter and more compact and further reducing costs.

[0015]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS Next, an embodiment of a vibration damper according to the present invention will be described with reference to the drawings. FIG. 1 is a block diagram showing a vibration suppression damper of the first embodiment. The vibration suppressing damper (hereinafter referred to as “vibration damper”) 1 controls a cylinder 10, a damping circuit for changing a flow resistance of a working fluid filled in a cylinder tube 11, and a switching of the damping circuit. Operating circuit.

First, the cylinder 10 has a cylinder tube 11 partitioned by a piston 12 into a head-side chamber 13 and a rod-side chamber 14. The piston 12 has a check valve that allows only the flow from the head-side chamber 13 to the rod-side chamber 14. 15 is formed. The piston rod 16 protruding from the rod side chamber 14 of the cylinder tube 11 has a cross-sectional area of the head side chamber 13 of the rod side chamber 1.
4 is designed to have a cross-sectional area that is twice as large as the cross-sectional area of the piston rod 4, and the amount of oil as the working fluid discharged from the cylinder is equal to the stroke when the piston rod 16 is extended and when it is contracted. I have.

The cylinder 10 is connected to the head-side chamber 1 via the oil tank 20 from the rod-side chamber 14.
A damping circuit (portion drawn by a solid line in the figure) for returning oil to 3 is connected. In the damping circuit, the head-side chamber 13 is connected to the oil tank 20 by a flow path 31, and the flow from the head-side chamber 13 to the oil tank 20 is restricted by a check valve 19 provided on the flow path 31. The other rod-side chamber 14 is connected to the oil tank 20 by a flow path 32 having a valve, an orifice, and the like.

The flow path 32 is provided with a filter 21 at the flow path 32a and connected to an input port of the fail-safe valve 22. The fail-safe valve 22 is an electromagnetic three-way valve that switches the oil flow in two directions. The fail-safe valve 22 communicates with the passive flow path 32b as shown in FIG. It is connected so as to communicate with the flow path 32c. On the passive flow path 32b, there is provided a passive orifice 23 having a relatively large diameter that reduces the flow resistance.
A bypass flow path 32d provided with a relief valve 24 set to a low pressure is connected. That is, the flow path 32b,
Reference numeral 32d denotes a passive orifice flow path in which the fail-safe valve 14 is turned off and the cylinder 10 functions as a passive damper when a power failure occurs.

On the other hand, the input flow path 32c is connected to the logic valve 25.
Connected to. The logic valve 25 enables large flow rate control with a small flow rate, and the input flow path 32c and the first output flow path 32e or the second output flow path 32
This is a mechanical control valve that can be connected to one of f. The logic valve 25 has a pilot line configured to mechanically control valve switching by a pressure difference on the second output flow path 32f side (signal input side 25P) connected to an operation circuit described later. That is, although the pilot line is not specifically shown, when the oil on the signal input side 25P stagnates and no pressure change occurs, the input flow path 32c is connected to the second output flow path 32f, and the signal input is performed. When the oil on the side 25P flows, the valve is switched so that the input flow path 32c and the first output flow path 32e are connected by the operating pressure.

The vibration damper 1 controls on-load and unload by switching the logic valve 25. The first output passage 32e is connected to the oil tank via the unload passage 32g. 20 and the second output passage 32f is connected to the electromagnetic variable relief valve 2
6 is connected to the oil tank 20 via an on-load flow path 32g provided with. Electromagnetic variable relief valve 26
Can control the pressure (damper force) by controlling the input current to the solenoid. Accordingly, the vibration damper 1 is configured to be unloaded when the oil passes through the first output flow path 32e, and is turned on when the oil passes through the second output flow path 32f. The operation circuit performs such switching between on-load and unload.

The operating circuit utilizes negative or positive pressure information transmitted from the head side chamber 13 when the piston rod 16 expands and contracts, thereby setting an operating pressure condition for controlling the logic valve 25. In this case, on-load / unload is mechanically selected. A first operating valve 27, which is an on-off solenoid valve, and a second operating valve 28, which is a three-way solenoid valve, are used in the operating circuit (portion drawn by a broken line in the figure), and the primary side of the first operating valve 27 is provided via a flow path 33A. It is connected to the head side chamber 13 of the cylinder 10. The secondary side of the first operating valve 27 is connected to the signal input side 2 of the logic valve 25 via the flow path 33B.
5P, the secondary side of the second operation valve 28 is connected to the pilot port of the operation check valve 29 via the flow path 33C, and to the oil tank 2 via the flow path 33D.
0g is connected to the unload channel 32g.

The operation check valve 29 is connected to the flow path 33B.
A flow path 33C is provided on a flow path 33E connected between the flow path 33D and a pilot flow path for controlling opening and closing. Operate check valve 29 is connected to flow path 3
The valve is opened by the oil flowing through 3C, and the oil flows from the flow path 33B, that is, from the signal input side 25P to the flow path 33D.

Next, the operation of the vibration damper 1 having such a configuration will be described. The damping damper 1 utilizes the flow resistance of the oil filled in the cylinder tube 11 when the cylinder 10 is interposed between the bogie and the vehicle body and the piston rod 16 expands and contracts due to vibration. Vibration of the vehicle body can be damped. That is, the rod side chamber 1
The oil discharged from 4 flows through the damping circuit, and attenuates the vibration of the vehicle body by the flow resistance when flowing back to the head side chamber 13 through the oil tank 20. At this time, the cylinder 10 constituting the vibration damper 1 is provided with the rod-side chamber 14 in any case where the piston rod 16 is expanded and contracted.
A certain amount of oil is discharged from the.

The fail-safe valve 22 is turned off as shown in FIG.
The normal operation state where the state is changed to the ON state will be described. In the vibration damper 1 of the present embodiment, four patterns of attenuation control can be performed by a combination of ON / OFF switching of the first operation valve 27 and the second operation valve 28. FIG. 2 shows the attenuation pattern. Hereinafter, each pattern will be described in order from the top. First, when the first operating valve 27 and the second operating valve 28 are in the ON state, both valves are switched from the illustrated closed state to the flow path 33.
B and 33C communicate with the flow path 33A to allow oil to flow from the head-side chamber 13 of the cylinder 10. this is,
In the first pattern shown in FIG. 2, the damping damper 1 is unloaded (does not generate a damping force in the damper) in both directions when the piston rod 16 is extended and contracted.

Therefore, when the cylinder rod 16 is extended, the pressure in the head side chamber 13 becomes negative and oil in the flow path 33B is sucked.
The P oil flows, and the logic valve 25 is switched to the first output flow path 32e by a change in the operating pressure. On the other hand, when the cylinder rod 16 contracts, the head side chamber 1
3 becomes positive pressure, and oil flows into the flow paths 33B and 33C. Then, the oil that has flowed into the flow path 33C opens the operation check valve 29, whereby the flow path 33B
Flows into the flow path 33D through the operation check valve 29. Therefore, logic valve 2
5, the oil on the signal input side 25P is also drawn by the operation check valve 29 and flows therethrough.
Switch to 2e side.

Therefore, the oil discharged from the rod side chamber 14 and flowing through the fail-safe valve 22 to the input flow path 32c flows through the logic valve 25 to the first output flow path 32e.
The oil flows into the oil tank 20 through the unload flow path 32g and returns. Since there is no flow resistance in the recirculating oil, the damper 1 does not generate damping force in any of expansion and contraction,
The vibration damper 1 is unloaded.

Next, when the first operating valve 27 and the second operating valve 28 are in the OFF state (the state shown in the figure), the flow path 33A and the flow paths 33B and 33C are shut off, and the operation circuit The oil in the head side chamber 13 does not flow. This is the second pattern shown in FIG. 2, in which the piston rod 16 is on-loaded (generates a damping force in the damper) in both directions when the piston rod 16 expands and contracts. Second
When the operation valve 28 is turned off, the flow paths 33C and 33D communicate with each other, and the oil in the flow path 33C returns from the flow path 33D to the tank 20 through the unload flow path 32g. Closes.

Therefore, when the cylinder rod 16 is extended, the head side chamber 13 becomes negative pressure and the oil in the flow path is sucked. However, the oil on the signal input side 25P blocked by the operation valves 27 and 28 is discharged. Since the flow does not flow, the logic valve 25 sets the input flow path 32c to the second output flow path 32f.
Side. On the other hand, when the cylinder rod 16 contracts, the head chamber 13 becomes positive pressure,
The oil therein does not flow into the flow paths 33B and 33C. Therefore, since the oil on the signal input side 25P does not flow, the logic valve 25 is configured such that the input flow path 32c is in the second position.
It is in a state of communicating with the output flow path 32f side.

Therefore, the oil discharged from the rod side chamber 14 and flowing through the fail-safe valve 22 to the input flow path 32c flows through the logic valve 25 to the second output flow path 32f.
It flows to the oil tank 20 through the on-load flow path 32h and is returned. At that time, the input current of the solenoid is controlled by the electromagnetic variable relief valve 26, and a predetermined flow resistance is generated according to the flow rate of the recirculating oil. for that reason,
The recirculating oil generates a damping force in both the expansion and contraction directions of the cylinder 10, and the vibration damper 1 is turned on.

Next, when the first operating valve 27 is ON and the second operating valve 28 is OFF, only the flow path 33B communicates with the flow path 33A. This is the third pattern shown in FIG. 2, in which the piston rod 16 is unloaded when it is extended, and is on-loaded when it is contracted. That is, when the cylinder rod 16 is extended, the head side chamber 13 becomes a negative pressure and the oil in the flow path 33B is sucked, so that the oil on the signal input side 25P flows, and the logic valve 25 changes due to a change in the operating pressure. Is the first output channel 32
Switch to e side.

On the other hand, when the cylinder rod 16 is contracted, the pressure in the head side chamber 13 becomes positive and the oil therein tries to flow into the flow path 33B, but the operation check valve 29 remains closed. . Therefore, the signal input side 2
Since the 5P oil does not flow, the logic valve 25 is in a state in which the separation 32c communicates with the second output flow path 32f side. Therefore, when the cylinder rod 16 is extended, the vibration damper 1 is unloaded and the cylinder rod 16
When the pressure is reduced, the recirculating oil passes through the electromagnetic variable relief valve 26, receives flow resistance, and becomes on-load, thereby generating a damping force.

Further, when the first operating valve 27 is in the OFF state and the second operating valve 28 is in the ON state, only the flow path 33C communicates with the flow path 33A. This is the fourth pattern shown in FIG. 2, in which the piston rod 16 is turned on when the piston rod 16 is extended, and unloaded when the piston rod 16 is contracted.
That is, when the cylinder rod 16 is extended, the head side chamber 13 becomes a negative pressure and the oil in the flow path 33C is sucked. The suction force acts to close the operation check valve 29. Therefore, since the oil on the signal input side 25P does not flow, the logic valve 25 is in a state where the separation 32c communicates with the second output flow path 32f.

On the other hand, when the cylinder rod 16 contracts, the pressure in the head-side chamber 13 becomes positive, and the oil therein flows into the flow path 33C. Therefore, the oil flows through the flow path 33D by opening the operation check valve 29, whereby the oil on the signal input side 25P is drawn and flows, and the change in the operating pressure causes the logic valve 25 to move to the first position.
It is switched to the output flow path 32e. Accordingly, the vibration damper 1 is unloaded when the cylinder rod 16 is contracted, and is turned on by the flow resistance due to the recirculating oil passing through the electromagnetic variable relief valve 26 when the cylinder rod 16 is extended. It becomes a load and damping force is generated.

Further, when the fail-safe valve 22 is in a non-energized state, that is, at the time of a failure such as a power failure, the oil discharged from the rod-side chamber 14 passes through the switched fail-safe valve 22 through the passive flow path 32b. From the oil tank 20 to reflux. Therefore, the recirculating oil is throttled by the orifice 23 on the passive flow path 32b to generate a predetermined flow resistance. The flow resistance at this time is not so large, and the vibration damper 1 functions as a passive damper that generates an appropriate damping force even at the time of a failure.

Therefore, according to the vibration damper 1 of the present embodiment, if the ON / OFF of the operation valves 27 and 28 is controlled, the cylinder rod 16 is controlled depending on the ON / OFF state.
The on-load or unload is uniquely determined as shown in FIG. That is, a mechanical HSSH type damper can be configured without the need for a separate stroke sensor for the damper and a sensor separately configured to obtain expansion / contraction information. For this reason, information regarding the expansion and contraction of the damper is not required in the calculation contents of the control device, and the calculation load is reduced. As a result, the calorific value of the calculation element is also reduced, and the control device can be downsized.

In addition, at the time of unloading, the oil flows through a logic valve 25 through which a large flow rate can flow, and the oil is recirculated without passing through other valves. Therefore, small-sized operation valves 27 and 28 can be selected. , The configuration of the valve block can be made compact. As a result, the number of vehicles in which the damper cannot be mounted in the running device for a railway vehicle, which has many restrictions on the mounting space, is reduced.

Next, a second embodiment of the vibration suppressing damper according to the present invention will be described. FIG. 3 is a block diagram showing a vibration damper according to the second embodiment. This vibration suppression damper (hereinafter, referred to as “damping damper”) 2 is obtained by changing the operation circuit of the damping damper 1 of the first embodiment. Therefore, the same components are denoted by the same reference numerals, and detailed description is omitted.

The operating circuit of the damping damper 2 (portion drawn by a broken line in the figure) has one operating valve 27, 28, which is two in the first embodiment, and therefore has an electromagnetic four-way valve. Is used as the operating valve 40. The operation valve 40 has a flow path 34A communicating with the head side chamber 13 and a second output flow path 32f of the logic valve 25.
, A flow path 34C that communicates with the pilot port of the operation check valve 29, and a flow path 34D that directly communicates with the oil tank 20. The operation check valve 29 is connected to the flow path 34B.
In order to control the flow of the oil inside, it is provided on a flow path 34E connected to the unload flow path 32g to the oil tank 20.

In the vibration damper 2 having such a configuration,
On-load and unload control is performed as follows. First, when the operation valve 40 is in the ON state, the flow path 34B is communicated with the flow path 34A by the operation valve 40, and when the piston rod 16 is extended, unloading is performed.
It becomes on-road when it shrinks. This corresponds to the third pattern shown in FIG. That is, when the cylinder rod 16 extends, the pressure in the head side chamber 13 becomes negative and the flow path 3
The oil in the signal input side 25P of the logic valve 25 flows because the oil in the 4A and 34B is sucked, and the logic valve 25 is switched to the first output flow path 32e by a change in the operating pressure.

On the other hand, when the cylinder rod 16 contracts, the pressure in the head side chamber 13 becomes positive and the oil therein tries to flow into the flow paths 34A and 34B, but the flow path 34C is shut off to operate. Since there is no flow for opening the check valve 29, no oil flows on the signal input side 25P. Therefore, the logic valve 25 is
2c is in communication with the second output flow path 32f. Therefore, when the cylinder rod 16 is extended, the vibration damper 1 is unloaded. When the cylinder rod 16 is contracted, the recirculating oil passes through the electromagnetic variable relief valve 26 and receives a flow resistance to turn on. It becomes a load and damping force is generated.

Next, when the operating valve 40 is in the OFF state (the state shown in the drawing), the operating valve 40 connects the flow path 34C to the flow path 34A and turns on when the piston rod 16 is extended. It becomes a load and unloads when it shrinks. This corresponds to the fourth pattern shown in FIG. That is, when the cylinder rod 16 is extended, the pressure in the head side chamber 13 becomes negative and the oil in the flow path 34C is sucked. The suction force acts to close the operation check valve 29. Therefore, the oil on the signal input side 25P does not flow.
Is in a state where the input flow path 32c communicates with the second output flow path 32f side.

On the other hand, when the cylinder rod 16 contracts, the pressure in the head-side chamber 13 becomes positive, and the oil therein flows into the flow path 34C. Therefore, the operation check valve 29 is opened and oil flows, whereby the oil on the signal input side 25P is drawn and flows, and the change in the operating pressure switches the logic valve 25 to the first output flow path 32e. Therefore, the vibration damper 1 has the cylinder rod 16
Is unloaded when the cylinder rod 1
When 6 is extended, the recirculating oil passes through the electromagnetic variable relief valve 26, receives a flow resistance, becomes on-load, and generates a damping force.

Further, when the fail-safe valve 22 is in a non-energized state, that is, at the time of a failure such as a power failure, the oil discharged from the rod side chamber 14 passes through the switched fail-safe valve 22 through the passive flow path 32b. From the oil tank 20 to reflux. Therefore, the recirculating oil is throttled by the orifice 23 on the passive flow path 32b to generate a predetermined flow resistance. The flow resistance at this time is not so large, and the vibration damper 2 functions as a passive damper that generates an appropriate damping force even at the time of a failure.

Therefore, according to the vibration damper 2 of the present embodiment, the mechanical HS
The effect of reducing the size of the control device associated with the configuration of the SH type damper, the compactness of the configuration of the valve block, and the reduction of the burden on the mounting work of the damper is achieved. Further, according to the vibration damper 2, the number of the operating valves can be reduced to one, so that the control efficiency is good, the driving current is saved, and the control device is downsized by reducing the driving amplifier capacity. In particular, the control device can be stored in the position of the bolster frame structure under the floor of the vehicle body.

Next, a third embodiment of the vibration suppressing damper according to the present invention will be described. FIG. 4 and FIG.
It is the block diagram which showed the damper for vibration suppression of embodiment. The vibration suppressing dampers (hereinafter referred to as "vibration dampers") 3 and 4 are provided with an orifice 41 having a small flow path diameter in the on-load flow path 32i and a relief valve 42 set to a low pressure in the bypass flow path 32j. This is a form in which the electromagnetic variable relief valve 26 used in the first embodiment is omitted.
The other components of the damping damper 3 shown in FIG. 4 are the same as those of the damping damper 1 of the first embodiment shown in FIG. 1, and the damping damper 4 shown in FIG. Is ON
The configuration is different in that the connection for / OFF is reversed. The same components as those in FIG. 1 are denoted by the same reference numerals, and detailed description is omitted.

As shown in FIG. 6, the vibration dampers 3 and 4 are offset from the center pin 50 connecting the vehicle body and the bogie to the front, rear, left and right, and are mounted in a direction opposite to the traveling direction X. However, although the dampers 3 and 4 are offset-disposed, the distance between the axis and the center pin 50 is about 200 mm, so that the dampers 3 and 4 can be considered to be disposed almost at the center of the bogie. .
The use of the two dampers may be either one or the other, but is an attachment method in which one of the dampers 3 and 4 can be backed up when the other fails.

Therefore, in such vibration dampers 3 and 4, during normal operation, on-load / unload is controlled as shown in FIG. 2 to attenuate vibration. However, regarding the vibration damper 4, the operating valve 27
'And 28' are reversed. Therefore, the on-load / unload control will be described below using only the vibration damper 3 shown in FIG. 4 as an example. First, when both the operation valves 27 and 28 in FIG. 4 are both ON, the flow paths 33B and 33C communicate with the flow path 33A, and the oil can flow from the head side chamber 13 of the cylinder 10. . This is the first pattern shown in FIG. 2, in which the piston rod 16 is unloaded in both directions when extended and retracted.

When the cylinder rod 16 is extended, the pressure in the head side chamber 13 becomes negative, and the oil in the flow path 33B is sucked and flows.
5P oil flows, and the logic valve 25 is switched to the first output flow path 32e by the change in the operating pressure. On the other hand, when the cylinder rod 16 contracts, the head side chamber 1
3 becomes positive pressure, and oil flows into the flow paths 33B and 33C. Then, the oil that has flowed into the flow path 33C opens the operation check valve 29, whereby the flow path 33B
Flows into the flow path 33D through the operation check valve 29. Therefore, logic valve 2
5, the oil on the signal input side 25P is also drawn by the operation check valve 29 and flows therethrough.
Switch to 2e side.

Therefore, the oil discharged from the rod side chamber 14 and flowing through the fail-safe valve 22 to the input flow path 32c flows through the logic valve 25 to the first output flow path 32e,
The oil flows back to the oil tank 20 through the unload flow path 32g and returns. However, since there is no flow resistance in the returning oil, no damping force is generated in any of the expansion and contraction of the damper 1. Is unloaded.

Next, when the first operation valve 27 and the second operation valve 28 are in the OFF state (the state shown in FIG. 4), the flow path 33A and the flow paths 33B and 33C are shut off, and the operation circuit is turned off. The oil in the head side chamber 13 does not flow. This is the second pattern shown in FIG. 2, in which the piston rod 16 is on-loaded in both directions when the piston rod 16 expands and contracts. When the second operation valve 28 is turned off, the flow paths 33C and 33D communicate with each other and the flow path 3
The oil in the 3C flows from the flow path 33D to the unload flow path 32g.
Return to the tank 20 through the
Closes.

Therefore, when the cylinder rod 16 is extended, the head side chamber 13 becomes negative pressure and the oil in the flow path is sucked. However, the oil on the signal input side 25P blocked by the operation valves 27 and 28 is discharged. Since the flow does not flow, the logic valve 25 sets the input flow path 32c to the second output flow path 32f.
Side. On the other hand, when the cylinder rod 16 contracts, the pressure in the head-side chamber 13 becomes positive, but the oil therein does not flow into the flow paths 33B and 33C. Therefore, the oil on the signal input side 25P also does not flow, and the logic valve 25 is in a state where the input flow path 32c communicates with the second output flow path 32f.

However, on the side of the second output flow path 32f of the logic valve 25, the flow paths 33B and 33E are shut off by the operation valve 27 and the operation check valve 29, and no oil flows through the logic valve 25.
The oil discharged from the rod side chamber 14 flows to the oil tank 20 through the on-load flow path 32i and returns. Accordingly, when the oil passes through the orifice 41, a flow resistance is generated in the recirculated oil, whereby a damping force is generated in both the expansion and contraction directions of the cylinder 10, and the vibration damper 1 is turned on.

Next, when the operation valve 27 is ON and the operation valve 28 is OFF, the flow path 33A,
Only 33B communicates. This is the third pattern shown in FIG. 2, in which the piston rod 16 is unloaded when it is extended, and is on-loaded when it is contracted. That is, when the cylinder rod 16 is extended, the head side chamber 13 becomes a negative pressure and the oil in the flow path 33B is sucked, so that the oil on the signal input side 25P flows, and the logic valve 25 changes due to a change in the operating pressure. Is switched to the first output flow path 32e side.

On the other hand, when the cylinder rod 16 is contracted, the pressure in the head side chamber 13 becomes positive and the oil therein tries to flow into the flow path 33B, but the operation check valve 29 is kept closed. . Therefore, the signal input side 2
Since the 5P oil does not flow, the logic valve 25 is in a state where the input flow path 32c communicates with the second output flow path 32f. Therefore, the vibration damper 1 has the cylinder rod 1
When the cylinder rod 16 is contracted, the recirculating oil flows to the orifice 41 when the cylinder rod 16 contracts.
Passing through, it becomes on-road due to flow resistance,
A damping force is generated.

Further, when the first operating valve 27 is in the OFF state and the second operating valve 28 is in the ON state, only the flow path 33C communicates with the flow path 33A. This is the fourth pattern shown in FIG. 2, in which the piston rod 16 is turned on when the piston rod 16 is extended, and unloaded when the piston rod 16 is contracted.
That is, when the cylinder rod 16 is extended, the head side chamber 13 becomes a negative pressure and the oil in the flow path 33C is sucked. The suction force acts to close the operation check valve 29. Therefore, since the oil on the signal input side 25P does not flow, the logic valve 25 is connected to the input flow path 32c.
Are in communication with the second output flow path 32f.

On the other hand, when the cylinder rod 16 contracts, the pressure in the head-side chamber 13 becomes positive and the oil therein flows into the flow path 33C. Therefore, the oil flows through the flow path 33D by opening the operation check valve 29, whereby the oil on the signal input side 25P is drawn and flows, and the change in the operating pressure causes the logic valve 25 to move to the first position.
It is switched to the output flow path 32e. Therefore, when the cylinder rod 16 is contracted, the vibration damper 1 is unloaded, and when the cylinder rod 16 is extended, the recirculating oil passes through the orifice 41 and receives a flow resistance, so that the damper 1 is on-loaded. Force is generated.

Therefore, according to the vibration damper 1 of the present embodiment, if the ON / OFF of the operation valves 27 and 28 is controlled, the cylinder rod 16 is controlled depending on the ON / OFF state.
The on-load or unload is uniquely determined as shown in FIG. That is, a stroke sensor for the damper and a sensor separately configured to obtain expansion / contraction information are not required, and a mechanical HSSH type damper can be configured. For this reason, information regarding the expansion and contraction of the damper is not required in the calculation contents of the control device, and the calculation load is reduced. As a result, the calorific value of the calculation element is also reduced, and the control device can be downsized.

Also, when unloading, the oil flows through the logic valve 25 through which a large flow rate can flow, and the oil is recirculated without passing through other valves. Therefore, small ones can be selected for the operation valves 27 and 28 and the like. , The configuration of the valve block can be made compact. As a result, the number of vehicles in which the damper cannot be mounted in the running device for a railway vehicle, which has many restrictions on the mounting space, is reduced.

On the other hand, when a failure such as a power failure occurs,
In the above-described damping damper 1 of the first embodiment, the fail-safe valve 22 allows the oil to flow back through the orifice 23 to function as a passive damper having a low reduction coefficient. In the dampers 3 and 4, the damper 3 is on-road, and the damper 4
Is unloaded, the damping damper 4 cannot function as a damper, and the damping damper 3 is a passive damper having a high damping coefficient.

However, as shown in FIG. 6, when two damping dampers are installed in one vehicle, the ratio of the damping coefficient of the damping damper 1 to the damping coefficient of the on-road damping damper 3 in the event of a failure. Is set to 1: 2, the damping coefficient of the vibration damper 1 becomes 2 in total, and the same damping ability can be obtained. For this reason, even if the damping damper 3 remains on-road with a high damping coefficient due to a failure, the ride comfort is not impaired, and the structure without the fail-safe structure is significantly reduced. It has been simplified, which has made it lighter and more compact, and also reduced costs. In addition, the vibration dampers 3 and 4 of the present embodiment can also reduce the size of the control device and the valve block as well as the mechanical HSH type damper in the same manner as in the first embodiment. Needless to say, the effect of reducing the burden on the mounting work of the damper is achieved.

When two dampers provided in one bogie are offset from the center of the bogie in the front-rear direction, the front damper with respect to the traveling direction X is on-road, and the rear damper is on-road. It has been confirmed by simulation and the like that if the damper is unloaded, high-speed running stability is improved as compared with the case where the damper is controlled in the same manner. Conversely, if the front damper is unloaded and the rear damper is on-road, the curve passing performance will be improved compared to the same control, as in simulations. Has been confirmed.
Therefore, the vibration dampers 1 to 4 of the first to third embodiments can be used.
In this case, the driving performance can be improved by reversing the on-load / unload control of the dampers arranged before and after the timing at which high-speed running stability is emphasized and the timing at which the curve passing performance is emphasized.

The embodiments of the vibration damper according to the present invention have been described above. However, the present invention is not limited to these, and various modifications can be made without departing from the gist of the present invention. is there.

[0063]

According to the present invention, since the pressure in the head-side chamber is used as the operating pressure of the mechanical control valve for switching between on-load and unloading, and the pressure is controlled by operating the operating valve, the vibration is made compact. It has become possible to provide a damper for suppression.

[Brief description of the drawings]

FIG. 1 is a block diagram showing a first embodiment of a vibration suppressing damper according to the present invention.

FIG. 2 is a diagram showing an attenuation pattern in a table.

FIG. 3 is a block diagram showing a second embodiment of a vibration damper according to the present invention.

FIG. 4 is a block diagram showing a third embodiment of a vibration damper according to the present invention.

FIG. 5 is a block diagram showing a third embodiment of a vibration damper according to the present invention.

FIG. 6 is a diagram showing an arrangement of two vibration suppression dampers.

[Explanation of symbols]

 1, 2, 3, 4 Vibration suppression damper 10 Cylinder 13 Head side chamber 14 Rod side chamber 20 Oil tank 22 Fail safe valve 23, 24 Orifice 26 Logic valve 27, 28 Operate valve 29 Operate check valve

Claims (6)

[Claims] 1. A cylinder in which a head-side chamber and a rod-side chamber communicate with each other through a flow path having a check valve formed in a piston, the head-side chamber and an oil tank are connected via a check valve, and the rod-side chamber is connected to the cylinder. An oil tank connected to the oil tank by a flow path having two paths forming an on-load and an unload, and a flow path forming the on-load and the unload can be switched by a mechanical control valve; A damper for suppressing vibration, comprising: an operating circuit for controlling pressure transmission to the mechanical control valve by operating pressure transmission in the head side chamber by expansion and contraction of a cylinder by an operating valve. 2. The electromagnetic variable relief valve according to claim 1, wherein the damping circuit adjusts a fluid pressure of a working fluid on an on-load flow path by controlling an input current to a solenoid. A damper for suppressing vibration, comprising: 3. The vibration damper according to claim 1, wherein the damping circuit has a passive orifice flow path that connects the head side chamber and the oil tank at the time of a failure.
A vibration-suppressing damper provided with a fail-safe valve for switching between the passive orifice flow path and the flow path forming the two paths of on-load and unload. 4. The damper for vibration suppression according to claim 1, wherein the operating circuit includes an electromagnetic on-off valve connected to the head side chamber and a pilot line of the mechanical control valve. An operation check valve for controlling a flow from a pilot line of a mechanical control valve to the unload side, and an electromagnetic three-way valve connected to the head side chamber, the check valve, and the unload side. Damper for vibration suppression. 5. The damper for vibration suppression according to claim 1, wherein the operating circuit is configured to control a flow from a pilot line of the mechanical control valve to the unload side. An electromagnetic four-way valve that connects the oil tank to the head side chamber and the pilot line of the check valve and the operating line of the mechanical control valve, and connects the head side chamber and the pilot port of the check valve by switching. A damper for vibration suppression characterized by having 6. A cylinder in which a head side chamber and a rod side chamber communicate with each other through a flow path including a check valve formed in a piston, the head side chamber and an oil tank are connected via a check valve, and the rod side chamber is connected to the cylinder. An oil tank connected to the oil tank by a flow path having two paths forming an on-load and an unload, and a flow path forming the on-load and the unload can be switched by a mechanical control valve; An electromagnetic on-off valve connected to a head side chamber and a pilot line of the mechanical control valve, an operation check valve for controlling a flow from the pilot line of the mechanical control valve to the unloading side, the head side chamber and the check valve, An operating circuit having an electromagnetic three-way valve connected to the unloading side; The two damping dampers for vibration suppression are mounted in one vehicle, and the ON / OFF states of the electromagnetic on-off valve and the electromagnetic three-way valve are reversed. Method.