KR100290627B1 - The damper and damping methods for damping the rolling of railroad cars - Google Patents

Abstract

An object of the present invention is to treat the damping force control in the damping force control circuit by using only the vehicle body speed signal of the vehicle body without using the damper speed signal, and even when the power is turned off. The damper for lateral vibration damping of railway vehicles, which can be controlled in common as a damping force control circuit as in the case of control without providing a dedicated circuit, can simplify the control system, reduce the number of parts, and reduce the size. It is to provide a damper and vibration damping method.

The solution of the present invention includes a cylinder (106) retrofitted between a bogie (A) and a vehicle body (B), and a rod-side chamber in a head side chamber 111 of the cylinder. A flow path 121 which allows only a flow of the working fluid flowing to the flow path 112, a reservoir 107 which passes through the suction valve 122 to the head chamber of the cylinder, and the head. A flow path 120 for communicating the side chamber to the reservoir, an unloading valve 118 for opening in the flow passage, and a damping force control circuit 8 interposed between the rod side chamber and the reservoir. The damping force control circuit is provided in parallel with the fixed contraction portion 126 and the fixed contraction portion, and continuously increases the relief set pressure as the input from the proportional solenoid 45 increases. Rail with proportional electronic relief valve (V) controlling from pressure to minimum pressure In the lateral vibration damping damper (C) of the vehicle, the proportional electromagnetic relief valve includes a valve case (7), an inlet port (32) and a return port (34 port) provided in the valve case, A valve seat 20 having a valve body 27 for intermittent communication between an inlet port and a return port, and a spring 30 for setting a relief pressure for applying a force in a direction in which the valve body closes. ), An adjusting screw body (9) for slidably installing a pressing body (17) for supporting the base of the spring, and an adjusting screw body (9) A locking member (19) for regulating the stroke of the pressing member, an adjusting blade (14) which is screwed into the adjusting screw to support the base end of the pressing member, and the pressing member And a hydraulic chamber (18) formed between the screw and the adjusting screw body, and a solenoid for applying a force in an open direction to the valve body. is located between the solenoid and the movable iron core 46 of the valve body and the solenoid, and in communication with the return port of the hydraulic chamber while pressing the valve body by the excitation of the solenoid. It is characterized by having a switching valve (切換 valve, 48) for switching to the communication of the inlet port.

Description

The damper and damping methods for damping the rolling of railroad cars}

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a semiactive control damper for damping lateral vibration generated in a vehicle body of a railway vehicle, and a damping method using the damper.

Semi-active control dampers and dampers for lateral vibration damping, which can effectively damp vibrations even when the mass of the body on the side where vibration is generated and the body that controls vibration, such as a railway vehicle, is extremely large. As a control system using the above, it is disclosed by Unexamined-Japanese-Patent No. 8-99634 and 8-239040, for example.

The control dampers disclosed in these publications include a stroke sensing cylinder which is opened between a bogie and a vehicle body, and from the head side chamber of the stroke sensing cylinder to a rod side chamber. A flow path that allows only a flow of the working fluid to flow, a reservoir that passes through the suction valve to the head chamber of the stroke sensing cylinder, and the head chamber communicates with the reservoir. Between the pressure side unloading valve opened in the flow passage, the new side unloading valve opened in the flow passage communicating the same rod side chamber to the head side chamber, and between the rod side chamber and the reservoir. It has a damping force control circuit retrofitted to it.

In the former damping force control circuit, a plurality of fixed orifices for generating a plurality of damping forces are arranged in series, and an opening and closing valve for controlling each fixed orifice is provided in parallel. Another latter damping force control circuit includes a fixed orifice and an always-open proportional valve or proportional pressure control valve that continuously controls proportionally the contraction opening. It is installed.

Each vibration damping system using the damper as described above includes a vehicle speed signal from a detector mounted on a vehicle body, a damper displacement signal from a stroke sensing cylinder, and a damper displacement signal from these. By using the calculated damper speed signal, the generated damping force of the damping force generating circuit is controlled by a computer, and at the same time, the lateral vibration of the railway vehicle is suppressed by controlling the new side unload valve and the pressure side unload valve.

In the former case, the on-off valve is switched by the computer according to the vehicle speed signal and the damper speed signal, and in the latter case, the proportional valve or the proportional control valve is continuously controlled by the computer with the same signal.

However, the control system is not particularly defective in function, but it is necessary to improve the following disadvantages.

First, the selective orifice switching valve or the proportional control of the proportional valve simultaneously changes the resistance of the fixed axial flow to generate a damping force. Therefore, the axial flow resistance of the fixed orifice passes through the operating oil ( It is determined by the flow rate of the product.

As a result, the flow rate of the hydraulic oil is proportional to the damper speed, so that the damper displacement signal is obtained using the stroke sensing cylinder, the damper speed signal is calculated by computer, and the damping force must be used to calculate the damping force. In other words, the stroke detection cylinder and its signal are necessarily required, which increases the size of the control system and increases the price.

Secondly, another dedicated damping force control circuit is provided to generate a predetermined damping force when the power is turned off to operate the stroke sensing cylinder as a normal damper. The dedicated damping force control circuit in this case is provided with a contraction, a relief valve and a switching valve, so that the number of parts is large, and the entire control system is enlarged and the price is increased. In addition, a dedicated control signal system is required for the switching control of the switching valve, and the control system is pluralized, thereby increasing the control system and increasing the price.

Therefore, the object of the present invention is that the damping force control in the damping force control circuit is processed using only the body speed signal of the vehicle body without using the damper speed signal, and the same control as when the power supply is turned off without a separate dedicated circuit. The present invention provides a damper and vibration damping method for lateral vibration damping of railway vehicles, which can be commonly controlled by a damping force control circuit, which simplifies the control system, reduces the number of parts, and can be miniaturized.

BRIEF DESCRIPTION OF THE DRAWINGS The block diagram of the lateral vibration damping system of the railway vehicle which concerns on this invention.

FIG. 2 is a circuit diagram of an embodiment of a damper for damping used in the damping system. FIG.

3 is a circuit diagram of a damping damper according to another embodiment as well.

4 is a longitudinal sectional front view of a proportional electromagnetic relief valve according to an embodiment of the present invention.

5 is a longitudinal sectional front view of a proportional electromagnetic relief valve according to another embodiment.

* Explanation of symbols for the main parts of the drawings

7: valve case 8: damping force control circuit

9: adjusting screw 14: adjusting screw

17: pressure body 18, 18a: hydraulic chamber

19: locking member 20: valve seat

27: valve body 30: spring

32: inlet port 34: return port

45: proportional solenoid 46: movable iron core

48, 48a: switching valve (切換 弁) 106: cylinder

107: reservoir 111: head side chamber

112: rod side chamber 117: check valve

118: pressure unloading valve

119: unloading valve for new side

120, 121: flow path 122: suction valve

130: Euro 131: check valve

A: Balance B: Body

C: Damper G: Computer

E: Detection means V: Proportional electronic relief valve

In order to achieve the above object, the damping damper of the present invention includes a cylinder that is opened between a bogie and a vehicle body, a flow path that allows only a flow of a working fluid flowing from the head side chamber of the cylinder to the rod side chamber, and a suction valve. A reservoir communicating with the head chamber of the cylinder through the cylinder, a flow passage communicating the head side chamber with the reservoir, an unloading valve for pressure side installed in the passage, and a damping force control circuit interposed between the rod side chamber and the reservoir. The control circuit is provided in parallel with the fixed contraction unit and the fixed contraction unit, and continuously increases the relief set pressure as the input from the proportional solenoid increases the relief set pressure. In the lateral vibration damping damper of a railway vehicle having a proportional electromagnetic relief valve controlled by the above, the proportional electromagnetic relief valve includes a valve case and a valve. A valve seat having an inlet port and a return port provided in the seat, a valve body for intermitting communication between the inlet port and the return port, a spring for setting a relief pressure for applying a force in a direction of closing the valve body, and a spring An adjustment screw body provided with a pressure body supporting a base end of the body so as to be slidable, and a stroke of the pressure body provided on the adjustment screw body; A retaining member for regulating the pressure, an adjustment screw for inserting the screw into the adjustment screw to support the base end of the pressure body, and a hydraulic chamber formed between the pressure body and the adjustment screw body. Iv), the solenoid which exerts a force in the opening direction with respect to the valve body, and the hydraulic chamber while pressing the valve body by the excitation of the solenoid, which is located between the valve body and the movable core of the solenoid. It is entrance gun by communication to return port Characterized in that the align switch valve for switching a communication path to the.

Similarly, other damping dampers include a cylinder that is opened between the bogie and the vehicle body, a flow path that allows only the flow of the working fluid flowing from the head side chamber of the cylinder to the rod side chamber, and a reservoir that communicates with the head side chamber of the cylinder through the intake valve. And a flow passage communicating the head side chamber to the reservoir, a pressure unloading valve installed in the flow passage, and a damping force control circuit interposed between the rod side chamber and the reservoir. The damping force control circuit includes a fixed shrinkage portion and a fixed shrinkage. In the horizontal vibration control damper of a railroad vehicle having a proportional electromagnetic relief valve which is installed in parallel to the part and controls the relief set pressure continuously from the highest pressure to the lowest pressure in accordance with the increase of the input from the proportional solenoid, the proportional electromagnetic relief valve The communication between the valve case, the inlet port and the return port installed in the valve case, the inlet port and the return port Adjustable valve body with sliding valve seat with valve body for intermittent operation, relief pressure setting spring for applying force in the direction of closing valve body, and adjusting screw for supporting base of spring And, between the solenoid which exerts a force in the opening direction with respect to the valve body, the hydraulic chamber made between the valve seat and the solenoid, and between the valve body and the movable core of the solenoid, pressing the valve body by the excitation of the solenoid, And a switching valve for switching from communicating with the return port of the hydraulic chamber to communicating with the inlet port.

In each of the damping dampers, a flow path that allows only a flow of the working fluid from the cylinder head side chamber to the rod side chamber is an unloading passage for the new side, and the off-load valve for the new side provided in the unloading passage is turned off. It is preferred to consist of a check valve installed in position.

Similarly, a flow passage allowing only the flow of the working fluid from the head side chamber of the cylinder to the rod side chamber may be composed of a flow passage provided in the piston and a check valve provided in the flow passage.

In addition, the lateral vibration damping method of a railway vehicle using the damper includes a cylinder that is opened between the bogie and the body, a flow path that allows only the flow of the working fluid from the head side chamber of the cylinder to the rod side chamber, and the inlet valve. A reservoir communicating with the head side chamber, a flow passage communicating the head side chamber with the reservoir, a pressure unloading valve opened in the passage, an unloading valve for the new side installed in the passage communicating the rod side chamber with the head side chamber, a rod side chamber, A damping force control circuit is provided between the reservoirs, and the damping force control circuit is installed in parallel with the fixed shrinkage portion and the fixed shrinkage portion, and the relief set pressure is continuously increased from the highest pressure to the lowest pressure in accordance with the increase in the input from the proportional solenoid. It has a proportional electronic relief valve to control up to, the proportional electronic relief valve is installed in the valve case, the valve case A valve seat having a valve body for intermitting communication between the inlet port and the return port, the inlet port and the return port, a spring for setting the relief pressure for applying a force in the closing direction of the valve body, and a pressure member for supporting the base of the spring. An adjustment screw body slidably installed, a locking member installed on the adjustment screw body to regulate the stroke of the press body, an adjustment screw for inserting the adjustment screw body into a screw type to support the base end of the press body, and the press body And the pressure chamber formed between the pressure adjusting chamber and the solenoid which exerts a force in the opening direction with respect to the valve body, and between the valve body and the movable iron core of the solenoid while pressing the valve body by the excitation of the solenoid. Using a damping damper equipped with a switching valve for switching from communication to the return port to communication to the inlet port, In accordance with only the signal on the vehicle body side such as the vehicle speed signal, the damping force value closest to the optimum value generated in the damping force control circuit is calculated by a computer, and the proportional electronic relief valve is proportionally controlled according to the calculation result. The vibration direction of the vehicle body is judged by a computer by the vehicle body speed, and the said unload valve for pressure side and the unload valve for a new side are selectively switched-controlled.

Similarly, another method includes a cylinder built between the bogie and the vehicle body, a flow path that allows only the flow of the working fluid from the head side chamber to the rod side chamber, a reservoir that passes through the suction valve to the head side chamber of the cylinder, and the head side chamber. The unloading valve for the new side installed in the flow passage communicating with the reservoir, the pressure unloading valve mounted in the flow passage, the unloading valve for the new side installed in the flow passage for communicating the rod side chamber with the head side chamber, and the damping force control circuit opened between the rod side chamber and the reservoir. The damping force control circuit has a fixed contraction portion and a proportional electromagnetic relief valve which is installed in parallel with the fixed contraction portion and continuously controls the relief set pressure from the highest pressure to the lowest pressure as the input from the proportional solenoid increases. The proportional electromagnetic relief valve includes a valve case, an inlet port and a return port installed in the valve case, an inlet port, Sliding valve seat with valve body for intermittent communication of ring port, Relief pressure setting spring for applying force in the direction of closing valve body, Adjusting screw body with adjustment screw for supporting spring base, Valve body The solenoid exerts a force in the open direction with respect to the valve seat, the hydraulic pressure chamber formed between the valve seat and the solenoid, and the valve body is pressed between the valve body and the movable core of the solenoid while pressing the valve body by the excitation of the solenoid, thereby returning the hydraulic pressure chamber. The highest value generated in the damping force control circuit by using a damping damper equipped with a switching valve for switching from communication to the port to communication to the inlet port, and only by signals from the vehicle body side such as the vehicle speed signal from the detection means installed in the vehicle body. Compute the damping force value that is closest to the computer using the proportional electronic relief valve To On the other hand, it is determined by the detecting unit to the vibrating direction of the vehicle body by the vehicle body speed to the computer characterized in that the selective switching control by the unload valve of the unloading valve and the pressure of the new cheukyong cheukyong.

DETAILED DESCRIPTION Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings.

In Fig. 1, the semi-active control dampers C and D according to the present invention are arranged horizontally between each other between the trolley A on the vibration generating side and the vehicle body B on the vibration damping side.

These semi-active control dampers C and D may be any one of them, but by using two as in this embodiment, a fail-safe effect is obtained in the case of one failure.

Moreover, the detector E which consists of an accelerometer or a speedometer which detects the vibration state of the said vehicle body B is provided in the vehicle body B of a vibration damping side.

The semi-active control dampers C and D comprise a cylinder 106, a reservoir 107 and a damping force control circuit 108 as shown in FIG.

The cylinder 106 partitions the inside of the cylinder 106 into the head side chamber 111 and the rod side chamber 112 by the free sliding piston 110, and simultaneously the piston rod 113 toward the outside from the piston 110. ) Is extended.

The semi-active control dampers C and D each have two unload valves 118 and 119 for pressing and for holding the position having the check valves 116 and 117 in the off position and the position for passing the flow path in the on position, respectively. Equipped with.

The pressure side unload valve 118 is opened in the middle of the flow path 120 that communicates between the head side chamber 111 and the reservoir 107, and is operated to flow from the head side chamber 111 to the reservoir 107 in an off position. The flow of fluid is prevented by the check valve 116, and the head side chamber 111 is arranged to communicate with the reservoir 107 as the flow path 120 at the on position.

On the other hand, the new side unload valve 119 is opened in the middle of the flow path 121 extending from the inlet side of the pressure side unload valve 118 toward the rod side chamber 112, and the cylinder 106 is turned off in the off position. The flow of the working fluid flowing from the rod side chamber 112 to the head side chamber 111 is prevented by the check valve 117, and the rod side chamber 112 is arranged to communicate with the head side chamber 111 in the on position.

The head side chamber 111 is also connected to the reservoir 107 by the suction flow passage 123 having the suction valve 122, and the rod side chamber 112 passes from the filter 124 through the damping force control circuit 108. Through the reservoir 107.

The damping force control circuit 108 has a proportional electronic relief that is continuously proportional to the fixed shrinkage portion 126 and the relief pressure that regulate the maximum generated damping force from the upstream rod side chamber 112 toward the downstream reservoir 107. The valves V are arranged in parallel.

Thus, in the low speed region when the piston 110 of the cylinder 106 starts to move, the working fluid extruded from the rod side chamber 112 to the damping force circuit 108 is first stored in the reservoir (126) through the fixed shrinkage portion 126. 107), the damping force is generated by the pressure loss.

Furthermore, when the piston speed enters the medium / high speed range, and the pressure loss reaches the relief set pressure of the proportional electromagnetic relief valve V arranged in parallel with the fixed shrinkage section 126, the valve body 27 opens and closes the operating fluid. The maximum damping force is controlled by flowing the reservoir 107 to keep the circuit pressure constant.

Therefore, by continuously operating the relief set pressure of the proportional electromagnetic relief valve V, it is possible to continuously change the maximum damping force regardless of the piston speed.

The proportional electromagnetic relief valve (V) has a force in the direction of closing the valve body (27) and the valve body (27) provided with opening and closing freely between the valve case (1), the inlet port (32) and the return port (34). To selectively communicate the spring 30 to which the pressure is applied, the hydraulic pressure chamber 17 provided on the distributing side of the spring 30, and the hydraulic pressure chamber 17 to the inlet port 32 and the return port 34. A switching valve 48 and a solenoid 45 for switching control of the switching valve 48 are provided.

As described above, if the lateral vibration of the vehicle body B occurs due to the lateral vibration of the truck A, and a relative displacement occurs between the truck A and the vehicle body B, Corresponding to the vibration directions of the trolley | bogie A and the vehicle body B, the cylinder 106 installed between these trolley | bogie A and the vehicle body B performs a telescopic motion.

When the cylinder 106 is extended, the working fluid in the reservoir 107 is sucked from the suction valve 122 to the head side chamber 111 through the suction passage 123, and the rod side chamber 112 The working fluid inside is extruded through the filter 124 toward the damping force control circuit 108.

On the contrary, in the case where the cylinder 106 performs the compression operation, the suction valve 122 is closed so that the working fluid in the rod side chamber 111 is transferred to the check valve of the unload valve 119 for the new side from the flow path 120. 117 is opened and flows to the rod side chamber 112, the working fluid of the amount corresponding to the intrusion volume of the piston rod 113 from the rod side chamber 112 passes through the filter 124 to control the damping force. Extrude into circuit 108. Then, the extruded working fluid toward the damping force control circuit 108 flows to the reservoir 107 under the control of the fixed contraction portion 126 and the proportional electromagnetic relief valve V described above.

Therefore, the damping force control circuit 108 generates a predetermined damping force by appropriately operating the proportional electromagnetic relief valve V in response to the relative lateral vibration speed between the bogie A and the vehicle body B. The lateral vibration of B) is effectively suppressed.

1, the detector E provided in the vehicle body B detects the vibration of the vehicle body B as a vehicle body signal T, and the vehicle body signal T is a processing circuit F for computer signal conversion. ) Is input to the computer G after being processed into a positive body speed signal U1 and a negative body speed signal U2.

In the case where the detector E is a speedometer, the process circuit F processes the positive body speed signal U1 and the negative body speed signal U2 as described above, but in the case of the accelerometer, the processing is performed. After the acceleration is converted into the speed by the circuit F, it is processed into a positive body speed signal U1 and a negative body speed signal U2.

On the one hand, the computer G judges the vibration direction of the vehicle body B at that time by the vehicle body speed signals U1 and U2 sent from the detector E on the vehicle body B side, and the valve driver circuit ( The switching signals P or Q are outputted to the pressure-loading or new-side unload valves 118 and 119 of the control valves C and C through the valve driver channels H and H to selectively control them on and off.

Similarly, the attenuation force closest to the optimum value generated in the damping force control circuit 108 is calculated by the computer G, and the result of the calculation is output as the control signal X, and the control signal X is solenoided. (45) is applied to proportionally control the electronic relief valve (V).

As described above, the semi-active control dampers C and C operate under the control as described below with respect to the lateral vibration generated between the bogie A and the vehicle body B, and perform a vibration damping action.

In the above control, however, the semi-active control dampers C and C have the same function as the action only when the respective operation directions are reversed.

Therefore, if only one operation is described, the other operation can be easily understood. Here, a damper system using one of the semi-active control dampers C is described below in order to prevent the confusing description.

① [when vehicle body B vibrates to the left]

If the vehicle body B vibrates to the left while traveling, the positive vehicle body speed signal U1 is input to the computer G through the processing circuit F in the detector E.

The computer G judges that the vehicle body B vibrates to the left in accordance with the positive vehicle speed signal U1, outputs a switching signal P to the pressure-loading unload valve 118, and turns it on. Switch to.

Here, if the trolley A vibrates to the left at a slower speed than the body B, or vibrates to the right opposite to the body B, the cylinder 106 operates on the extension side to control the damping force of the internal working fluid. Extrude into circuit 108.

When the lateral vibration speed is within the normal range, the vehicle body B sends the control signal X corresponding to the lateral vibration speed from the computer G to the electronic relief valve V to provide the relief pressure as described above. While controlling, the working fluid extruded from the cylinder 106 to the damping force control circuit 108 is controlled in accordance with the control operation of the fixed shrinkage portion 126 and the proportional electromagnetic relief valve V to control the generated damping force at that time. Suppresses the lateral vibration of).

On the other hand, when the vehicle body B vibrates to the left, for example, if the vehicle body B vibrates to the left at a speed faster than the lateral oscillation speed due to the deviation of the trolley A from the rail, etc., The cylinder 106 compresses, and the fluid pressure corresponding to the generated damping force of the damping force control circuit 108 is also generated in the head side chamber 111 of the cylinder 106.

The fluid pressure generated in the head side chamber 111 is caused by the difference in the hydraulic pressure area between the head side chamber 111 and the rod side chamber 112 generated by the presence of the piston rod 113 of the cylinder 106. It acts as a pushing force toward the extension direction and causes the vehicle body B to vibrate further to the left, so that the fluid pressure needs to be prevented from occurring.

However, even in this case, since the vehicle body B itself vibrates to the left side, the computer G is connected to the unload valve 118 for the pressure side in response to the positive vehicle speed signal U1 of the detector E. The switching signal P is continuously output, and the pressure unload valve 118 is kept at the on position.

As a result, the working fluid of the head side chamber 111 flows from the flow path 120 to the reservoir 107 via the pressure side unload valve 118.

As a result, no fluid pressure is generated in the head side chamber 111 of the cylinder 106, and the cylinder 106 is prevented from vibrating the vehicle body B further to the left.

② [When body B vibrates to the right]

In contrast to the above, when the vehicle body B vibrates to the right, the negative vehicle body speed signal U2 is input to the computer G by the detector E. FIG.

In response to this negative body speed signal U2, the computer G outputs a switching signal Q to the new-side unload valve 119 this time and switches it to the on position.

Here, when the trolley A vibrates to the right at a slower speed than the vehicle body B, or vibrates to the left as opposed to the vehicle body B, the cylinder 106 operates on the compression side to control the damping force of the internal working fluid. Extrude toward circuit 108.

The computer G outputs the control signal X according to the negative vehicle body speed signal U2 as in the case where the vehicle body B vibrates from the left side, thereby reducing the relief pressure of the proportional electromagnetic relief valve V. By proportional control, the generated damping force of the damping force control circuit 108 is appropriately controlled to effectively suppress lateral vibration to the right side of the vehicle body B. FIG.

③ [Uncontrollable due to power off or abnormal situation]

Also in this case, since the cylinder 106 repeats the stretching operation in response to the vibration in the left and right directions of the vehicle body B, the working fluid inside is extruded toward the damping force control circuit 108.

However, when the power is turned off or when the standby signal disappears, the switching signals P and Q and the control signal X in the computer G are also cut off. The side unload valves 118 and 119 and the proportional electronic relief valve V maintain the off position of FIG.

In this way, the working fluid extruded from the cylinder 106 to the damping force control circuit 108 flows to the reservoir 107 through the fixed shrinkage portion 126, and the pressure loss of the shrinkage portion 126 is a proportional electromagnetic relief valve. The damping set pressure at the off position of (V) generates a predetermined damping force, moves to a normal damper, and has a double safety effect by damping vibration in the left and right directions of the vehicle body (B).

3 shows another embodiment of the present invention.

In FIG. 2 described above, in the compression operation of the cylinder 106, flow paths 120 and 120 provided outside to flow paths for allowing the working fluid to flow from the head side chamber 111 toward the rod side chamber 112. And the check valve 117 provided at the off position of the new side unload valve 119.

On the other hand, in the embodiment shown in FIG. 3, the push-side and new-side unload valves 118 and 119 and the check valves 116 and 117 provided in the off position are removed, respectively, and the off position is set to the block position.

And instead, the flow path 130 which communicates the head side chamber 111 and the rod side chamber 112 is formed with respect to the piston 110 of the cylinder 106, and the head side chamber 111 with respect to this flow path 130 is provided. ), A check valve 131 is disposed in the housing that allows only the flow of the working fluid toward the rod side chamber 112.

In this manner, the cylinder 106 also closes the suction valve 122 during the compression operation and causes the working fluid in the head side chamber 111 to flow to the rod side chamber 112 by opening the check valve 131 in the flow passage 130. In addition, in the rod side chamber 112, the amount of the working fluid corresponding to the intrusion volume of the piston rod 113 is extruded through the filter 124 into the damping force control circuit 108.

Thus, also in the embodiment of Fig. 3, the cylinder 106 acts as a damper in one direction flow as in the case of the previous embodiment.

Next, an embodiment of the proportional electromagnetic relief valve V will be described.

4 shows one embodiment of a proportional electromagnetic relief valve (V). The proportional electromagnetic relief valve (V) has three annular grooves (2, 3, 4) and annular projections (5) between the annular grooves 3 and 4 in parallel with the axial direction. An outer portion is formed by the valve case 7 having the through bore 6 formed therein. This proportional electromagnetic relief valve V is connected to the damping force control circuit 108 of FIG. 2 or FIG. 3 and communicates with the inlet port 32 and the reservoir 107 which communicate with the head side chamber 112 of the cylinder 106. The return port 34 is provided.

The opening of one end of the bore 6 is closed by the adjusting screw body 9 inserted into the feed screw 8 so as to freely advance and retreat, and furthermore, the adjusting screw body 9 The annular groove (2) is inserted into the seal (10, 11) to maintain the oil tight state.

Inside the adjustment screw 9, a hole 12 having a large diameter is formed alternately from the inner end to the middle, and penetrates the adjustment screw 9 from the outside to form the hole 12. The adjustment screw 14 is screwed in while maintaining the oil tight state by refitting the seal 13 facing the inside of the valve.

The adjusting screw (9) and the adjusting screw (14) are provided with independent stop nuts (15, 16), respectively, and these stop nuts (15, 16) are used for the valve case (7) and the adjusting screw (9). And between the adjusting screw body 9 and the adjusting screw 14 can be freely locked in any relative positional relationship.

In the adjusting screw body 9, the press body 17 is inserted into the hole 12 so that sliding is free, and the hydraulic chamber 18 is partitioned at the proximal end, and at the outlet part, an annular locking member ( 19) is screwed so as to limit the sliding range of the press body 17 while cooperating with the tip of the adjustment blade 14 described above.

On the other hand, from the opening part of the other end of the bore 6, the valve seat 20 and the single end | piece 21 are opened, the seal 56 is opened between them, and it is sequentially inserted side by side in the axial direction, The valve seat 20 is sandwiched between the annular protrusion 5 provided on the bore 6 and the end 21 by pushing the screw into the end 21 while maintaining the oil tight state with the seal 22. Place it fixed.

In addition, in this embodiment, the valve seat 20 is provided with a restricting cylinder 23 arranged side by side in the axial direction at the distal end side, and the proximal end of the restricting cylinder 23 is provided as a single stage 21. It presses and fixes to the annular protrusion 5 of the bore 6.

In this manner, the seal 24, which is opened between the valve seat 20 and the restriction cylinder 23, is pressed against the inner wall surface of the bore 6, and the valve seat 20 is attached to the seal 24. The maximum screw insertion position of the adjusting screw body 9 by limiting the tip of the restricting cylinder 23 to the above-mentioned adjusting screw body 9 while maintaining the oil-tight state between the inner wall surface of the bore 6 and the bore 6. Do it.

The valve seat 20 includes an axial through hole 25 located in the center portion and a through flow path 26 parallel thereto, and at the inner end of the through hole 25, the valve seat 27 is formed. The valve body 27 is supported by inserting the guide member 28 so that sliding is free.

A labyrinth groove 29 is provided on the outer circumferential surface of the guide portion 28 in the valve body 27 to seal between the through hole 25 and to seal the valve body. The relief pressure setting spring 30 is opened between the 27 and the press body 17, and the valve body 27 is pressed against the valve seat 20 by the relief pressure setting spring 30. The inner end of the through hole 25 opposite to the guide member 28 is closed.

The through hole 25 is an inlet port for introducing a circuit pressure introduced from the annular groove 4 to the valve case 7 through a hole 31 provided in the valve seat 20. The annular groove on the valve case 7 side passes through the opening 32 and resists the relief pressure setting spring 30 to open and press the valve body 27 to open the hole 33 provided in the restricting cylinder 23. (3) through the return port (34).

In addition, in parallel with the above, the annular groove 4 leading to the inlet port 32 is connected to the valve case 7 and the single stage 21 through a flow path 35 provided in the valve case 7. A flow path 38 extending through the annular flow passage 36 formed therebetween and extending in a radial direction with the annular groove 37 provided on the outer circumferential surface of the single end 21 in the annular flow passage 36. It communicates with the through-hole 39 provided toward the axial direction of the center part of single end 21 through the following.

In addition, the through hole 39 has a through passage 26 of the valve seat 20, an oil hole 33 of the restricting cylinder 23, and an annular groove 3 of the valve case 7. Communication provided to the valve case 7 through the flow path 41 and the annular groove 42 which are connected to the return port 34 and separated from the flow path 38 as the seal 40 in the single end 21 through the return port 34. Through the flow path 43, the annular groove 2 also leads to the hydraulic chamber 18 on the back side of the press body 17. As shown in FIG.

On the other hand, at the outer end of the end piece 21, the solenoid 45 is screwed with the seal 44 held in an oil-tight state, and the opening 21 and the solenoid 45 are proportional to each other. At the same time, a solenoid is provided, and a predetermined switching gap 47 is provided between the movable iron core 46 of the proportional solenoid 45 and the guide portion 28 of the valve body 27. The switching valve 48 is accommodated in the through hole 39 in the 21.

When the solenoid 45 is turned off, the switching valve 48 penetrates the flow path 41 and the valve seat 20 of the single end 21 by a spring 49 interposed between the single end 21 and the single end 21. The flow path 26 is offset to a retracted position communicating with the return port 34 through the hole 33 of the restricting cylinder 23 and the annular groove 3 of the valve case 7.

Then, the switching valve 48 is pressed against the spring 49 by the movable iron core 46 along with the excitation of the solenoid 45, and the flow passage 41 communicating with the return port 34 is communicated with the flow passage 38 until then. The hydraulic pressure chamber 18 on the back side of the press body 17 is switched to communicate with the inlet port 32.

In addition, while simultaneously filling the switching gap 47 to press the guide portion 28 of the valve body 27, a force is applied to the valve body 27 in the direction in which the input from the solenoid 45 opens. The apparent spring force of the relief pressure setting spring 30 is lowered by the force in the direction to control the height of the relief setting pressure of the valve body 27.

Next, the effect of the proportional electromagnetic relief valve V by the Example of FIG. 3 comprised as mentioned above is demonstrated.

Here, the adjustment operation to the maximum pressure of the relief set pressure in the proportional electromagnetic relief valve (V), first pushes the pressure adjusting member (17) along the adjusting screw (9) by pushing the adjusting screw (14) with screws. The tip of the press body 17 is pressed against the locking member 19 provided on the adjusting screw body 9 to bring it into close contact.

Subsequently, in this state, this time, the adjusting screw body 9 is rotated and moved back and forth with the adjusting screw 14 and the pressing body 17 by the feed screw 8, thereby pressing the pressing body 17. And the spring force of the relief pressure setting spring 30 installed between the valve body 27 and the valve body 27 are changed to set the spring force to a desired value.

On the other hand, the intermediate pressure of the relief setting pressure at the time of the solenoid 45 turning off retracts the adjustment part 14 in the said state, and extends the spring length of the spring 30 for relief pressure setting, By lowering the force to a desired value, it is set to an arbitrary relief set pressure which is lower than the previous maximum pressure and higher than the minimum pressure determined according to the maximum input from the solenoid 45.

On the other hand, when using in this state, when the solenoid 45 is turned on to flow a small current, the solenoid 45 starts to operate, and the switching valve 48 is switched to the movable core 46, While the input from the solenoid 45 is applied to the guide portion 28 of the valve body 27 via the switching valve 48, the flow paths 38 and 41 communicate with each other and the hydraulic pressure chamber 18 returns to the return port 34. Is switched to the communication to the inlet port (32).

However, at this time, at the small current value, the input from the solenoid 45 applied to the guide portion 28 of the valve body 27 away from the switching valve 48 is extremely small and resists the switching valve 49 against the spring 49. Since it is consumed only by switching the 48, the force can be applied to the guide portion 28 of the valve body 27 by simply filling the switching gap 47 and switching the switching valve 48. Not far

Even so, the circuit pressure from the inlet port 32 is guided to the hydraulic chamber 18 by the switching of the switching valve 48 through the switching valve 48, so that the relief pressure setting spring 30 is pressed. While pressing, leaving the adjustment bar 14 intact, the press body 17 is pushed forward, and the press body 17 is pressed against the locking member 19 provided on the adjusting screw body 9 to bring it into close contact.

Thereby, the positional relationship between the press body 17 and the valve seat 20 becomes completely the same as when the previously described relief setting pressure is set to the maximum pressure, and with it, the spring of the relief pressure setting spring 30 Since the length is also the same, the relief set pressure at that time maintains the maximum pressure.

In addition, if the current value applied to the solenoid 45 in the above state is increased, the input from the solenoid 45 to the guide portion 28 of the valve body 27 is usually increased in proportion to it, and the relief set pressure is increased. As a result, the pressure drops continuously.

In operation, if the solenoid 45 is turned off due to a failure or any other reason, the input from the solenoid 45 becomes zero, and the switching valve 48 is in the original state due to the restoring force of the spring 49. The hydraulic pressure chamber 18 switches to the communication of the return port 34.

In this way, the circuit pressure at the inlet port 32 applied to the hydraulic chamber 18 is cut off and communicated to the low pressure side, and the pressing body 17 is pressed by the relief pressure setting spring 30. It retracts and retracts to the position which contact | connects the adjustment 14.

In this state, the positional relationship between the press body 17 and the valve seat 20 is exactly the same as the state when the relief setting pressure described above is set to the intermediate pressure, and the spring 30 for setting the relief pressure is Since the spring length is also the same length, the relief set pressure at that time is not only lower than the maximum pressure but also becomes an intermediate pressure higher than the minimum pressure determined by the maximum input from the solenoid 45.

In this way, during normal operation, while performing the predetermined control as the proportional electromagnetic relief valve 1, the relief set pressure when the solenoid 45 is turned off by any other defect is set to an arbitrary intermediate pressure. It is possible to eliminate the disadvantages in that it is impossible to fully exhibit the performance as a device while maintaining the minimum control force required by the position.

5 shows the proportional electromagnetic relief valve V which is the form of another embodiment by this invention, and the basic structure is the same as that of the proportional electromagnetic relief valve V of the Example shown in FIG. Here, only different parts will be described in order to avoid duplication of explanation.

In the proportional electromagnetic relief valve V shown in FIG. 5, as in the embodiment of FIG. 4, a pressurizing body 17 is provided between the adjustment lever 14 and the spring 30 for setting the relief pressure. Instead of the hydraulic pressure chamber 18, the base end of the spring 30 for setting the relief pressure is held by the adjustment guide 14 to immediately support the screw support 30a.

Instead, the projection 50 is formed on the front end side of the end piece 21a to sandwich the proximal end of the valve seat 20a, and only the valve seat 20a is provided between the adjusting screw body 9a and the single end 21a. The hydraulic chamber 18a is formed between the bore 6 of the valve case 7 so that sliding is free and between the end 21a of the solenoid 45.

Then, the oil pressure chamber 18a is provided with the oil hole 33a and the valve case of the adjustment screw 9a by the oil passage 26a provided in the valve seat 20a through the inside of the switching valve 48a in the oil passage 41a. The annular groove (3) communicates with the return port (34), and also communicates with the flow paths (38, 41a) in accordance with the switching operation of the switching valve (48a) to communicate with the hydraulic chamber to the return port (34). It is configured to switch from the communication to the inlet port.

Also in the proportional electromagnetic relief valve V shown in FIG. 5 configured as described above, the adjustment operation of the maximum pressure of the relief set pressure is first performed by screwing the adjusting screw 9a to the valve seat 20a and the bore 6. It presses forward along the protrusion part 50 of the end piece 21a, and presses the base end of the said valve seat 20a to the end piece 21a by the solenoid 45, and it contacts.

Then, in this state, this time, the adjustment knob 14 is rotated to change the spring length of the spring 30 for setting the relief pressure, and the spring force of the spring 30 for setting the relief pressure is set to a desired value. By setting it.

Further, when the proportional solenoid 45 is turned off, the intermediate pressure of the relief setting pressure is moved forward by adjusting the adjusting screw body 9a while following the adjustment guide 14 in the above state, so that the spring 30 for relief pressure setting is By extending the spring length, as the spring force is lowered to a desired value, it is set to any relief set pressure not only lower than the previous maximum pressure but higher than the minimum pressure determined by the maximum input from the solenoid 45.

When the solenoid 45 is turned on to flow a small current, the solenoid 45 starts to operate to switch the switching valve 48a, and the solenoid 45 through the switching valve 48a. ), The hydraulic pressure chamber 18a is switched from communicating with the return port 34 to communicating with the inlet port 32 while applying the input from the valve body 27 to the guide portion 28 of the valve body 27.

As a result, the circuit pressure at the inlet port 32 is guided to the hydraulic pressure chamber 18a through the switching valve 48a. Therefore, the valve seat 20a is pressed while pressing the spring 30 for setting the relief pressure. Press to advance, and press the valve seat 20a against the tip of the adjusting screw body 9a.

This state is the same as the state where the positional relationship between the adjusting screw body 9a and the valve seat 20a is set when the relief setting pressure described above is set to the maximum pressure, and the spring of the spring 30 for setting the relief pressure is Since the length is also the same, the relief set pressure at that time becomes the maximum pressure.

In addition, when the current value applied to the solenoid in this state is increased, the input from the solenoid 45 to the guide portion 28 of the valve body 27 is almost proportional to that in the case of the embodiment of FIG. Increasingly, the relief setting pressure is continuously lowered toward the lowest pressure.

On the other hand, when the solenoid 45 is turned off due to a failure or any other reason during the above operation, the switching valve 48a is switched to the original state so that the hydraulic chamber 18a communicates with the return port 34. do.

In connection with this, since the circuit pressure in the inlet port 32 added to the hydraulic chamber 18a is cut off, and a pressure falls, the valve seat 20a follows the valve body 37, and the spring 30 for relief pressure setting is carried out. It is pressed by, and it moves away from the adjustment screw body 9a to the last retreat position which abuts on the single end 21a of the solenoid 45. As shown in FIG.

In this case, however, when the proportional electromagnetic relief valve V is in the relief operation state, the valve body 27 is separated from the valve seat 20a to open the through hole 25. The valve seat 20a cannot be pushed back through the valve body 27 by the spring 30 for pressure setting.

Therefore, in the case of the use form which may cause such a state, as shown in FIG. 5, the return spring 55 is retrofitted between the adjusting screw 9a and the valve seat 20a, and this return spring is carried out. It is preferable to move the valve seat 20a to the last retracted position in contact with the single end 21a of the solenoid 45 with the spring force of.

In addition, the above-mentioned state is also the same as the state where the positional relationship between the adjusting screw 9a and the valve seat 20a is the same as the state when the relief setting pressure described above is set to the intermediate pressure. Since the spring length of the spring 30 is also the same, the relief set pressure at that time is not only lower than the maximum pressure but also becomes an intermediate pressure higher than the minimum pressure determined by the maximum input from the solenoid 45.

In this way, during normal operation, while performing the predetermined control as the proportional electromagnetic relief valve (V), the relief set pressure when the solenoid 45 is turned off due to any other defect is set to an arbitrary intermediate pressure. In this way, it is possible to eliminate the defect that the device cannot fully exhibit its performance while ensuring the minimum control force required by the device.

4 and 5 described so far, the flow paths 26 and 26a of the valve seats 20 and 20a and the space portions on both sides of the movable core 46 of the solenoid 45 are connected. The damping holes 52 and 53 are provided in the flow path 51, and these damping holes are for stabilizing the operation as the proportional electromagnetic relief valve V. FIG.

In the middle of the flow path 35, a check valve 54 for preventing the reverse flow of the working medium from the annular flow path 36 to the inlet port 32 is provided. These check valves 54 are proportional electromagnetic relief valves. During the operation of (V), the pressure on the inlet port 32 side drops to the pressure on the return port 34 side. As a result, the pressure in the hydraulic chambers 18 and 18a decreases, and the relief set pressure becomes an intermediate pressure. It is to prevent throwing away.

Therefore, including the feedback spring 55 in Fig. 5 described above, these damping holes 52, 53 and the check valve 54 are such a necessity from the use aspect of the proportional electromagnetic relief valve V. Of course, if you do not have a good installation.

According to the present invention has the following effects.

(1) According to the damping damper according to the present invention and the damping method using the damper, a damping force control circuit is provided in parallel with the fixed shrinkage portion and the fixed shrinkage portion, and the relief according to the increase in the input from the proportional solenoid 45 is achieved. Since it has a proportional electronic relief valve that continuously controls the set pressure from the highest pressure to the lowest pressure, there is no need to use damper displacement detection means such as a stroke sensing cylinder, and a damper speed signal is required for damping force control. In this case, the number of parts is small, and the whole vibration suppression system is made small, thereby reducing the cost.

(2) Similarly, the damper damper power damper generates a predetermined damping force when the power is turned off and functions as a normal damper. Therefore, it is not necessary to install another dedicated damping force control circuit, thereby miniaturizing it and lowering the price. have. In other words, when the power is turned off, the proportional electronic relief valve can freely set the characteristic when the power is turned off within the range of the characteristics when the power is turned off, eliminating the need for other damping force control circuits and special control when the power is turned off, thereby simplifying the control system. As a result, the size of the control system can be reduced and the price can be reduced.

Claims (6)

It allows only the flow of working fluid from the head side chamber of the cylinder to the rod side chamber, between the cylinder and the body of the cylinder. Reservoir passing through the head chamber of the cylinder via a flow path, a suction valve, a flow path through which the head side chamber communicates with the reservoir, and a pressure-compression opening built in the flow path. An unloading valve and a damping force control circuit interposed between the rod side chamber and the reservoir. The damping force control circuit includes a fixed contraction unit and a fixed contraction unit. A proportional solenoid relief valve that is installed in parallel to the relief solenoid to control the relief set pressure continuously from the highest pressure to the lowest pressure as the input from the proportional solenoid increases. Of railway vehicles In the damper for lateral vibration damping, the proportional electromagnetic relief valve includes a valve case, an inlet port and a return port provided in the valve case, and an inlet. A valve seat having a valve body for intermittent communication between the port and the return port, a spring for setting the relief pressure for applying a force in the closing direction of the valve body, and a base of the spring. An adjusting screw body provided with a supporting pressing body slidably, and a locking member provided on the adjusting screw body to regulate the stroke of the pressing body. And the adjustment thread which is screwed into the adjusting screw body to support the base end of the pressing body, the hydraulic chamber formed between the pressing body and the adjusting screw body, and the valve body. The solenoid that exerts force in the open direction and the valve body and solenoid A switching valve which is located between the movable cores and switches from communicating with the return port of the hydraulic chamber to the inlet port while pressing the valve body by the excitation of the solenoid ( A damping damper for lateral vibration damping of a railway vehicle, characterized by having a valve. A cylinder that is opened between the bogie and the vehicle body, a flow path that allows only a flow of the working fluid from the head side chamber of the cylinder to the rod side chamber, a reservoir through the suction valve to the head side chamber of the cylinder, and the head side chamber communicate with the reservoir. And a damping force control circuit mounted between the rod side chamber and the reservoir. The damping force control circuit is provided in parallel with the fixed shrinkage portion and the fixed shrinkage portion. In the damper for lateral vibration damping of a railway vehicle having a proportional electronic relief valve that continuously controls the relief set pressure from the highest pressure to the lowest pressure in accordance with an increase in the input of the proportional solenoid, the proportional electromagnetic relief valve is a valve case. And a valve body for controlling the communication between the inlet port and the return port provided in the valve case and the inlet port and the return port. A valve seat for possible adjustment, a spring for setting the relief pressure for applying force in the direction of closing the valve body, an adjustment screw body for adjusting the spring to support the proximal end of the spring, a solenoid for applying force in the opening direction to the valve body, and a valve Located between the hydraulic chamber formed between the seat and the solenoid, and between the valve body and the movable iron core in the solenoid, switching from communication to the inlet port to communication with the inlet port while pressing the valve body by excitation of the solenoid. A damper for lateral vibration damping of a railway vehicle, characterized by a switching valve. The flow path for allowing only the flow of the working fluid from the head side chamber of the cylinder to the rod side chamber is provided in the unloading flow path for the new side and the unloading flow path. A damper for lateral vibration damping of a railway vehicle, comprising a check valve installed at an off position of a new unload valve. 3. The railway vehicle according to claim 1 or 2, wherein the flow passage allowing only the flow of the working fluid from the head side chamber of the cylinder to the rod side chamber is composed of a flow passage provided in the piston and a check valve provided in the flow passage. Transverse vibration damper. A cylinder that is opened between the bogie and the vehicle body, a flow path that allows only a flow of the working fluid from the head side chamber of the cylinder to the rod side chamber, a reservoir through the suction valve to the head side chamber of the cylinder, and the head side chamber communicate with the reservoir. And an unload valve for the pressure side installed in the passage, an unload valve for the new side in the passage communicating the rod side chamber with the head side chamber, and a damping force control circuit interposed between the rod side chamber and the reservoir. The damping force control circuit has a fixed contraction portion and a proportional electromagnetic relief valve which is provided in parallel with the fixed contraction portion and controls the relief set pressure continuously from the highest pressure to the lowest pressure in accordance with an increase in the input from the proportional solenoid. The proportional electronic relief valve is connected to the valve case, the inlet port and the return port provided in the valve case, and the inlet port and the return port. Valve seat with valve body for clamping the valve, spring for relief pressure setting to apply force in the direction of closing the valve body, adjustment screw body for slidably installing a pressure body supporting the spring base, and adjustment screw body A locking member which is provided in the control member and restricts the stroke of the press body, an adjustment screw which is screwed into the adjusting screw body to support the base end of the press body, a hydraulic chamber formed between the press body and the adjusting screw body, and the valve body. Switching between communication from the return port of the hydraulic chamber to the inlet port while pressing the valve body by the excitation of the solenoid, which is located between the solenoid exerting a force in the open direction and the valve core and the movable core of the solenoid. Damping force control using a damping damper equipped with a valve, according to only the signal on the vehicle body side such as the vehicle speed signal from the detection means provided on the vehicle body. The computer calculates the damping force value closest to the optimum value generated in the circuit, and proportionally controls the proportional electronic relief valve according to the calculation result, and determines the vibration direction of the vehicle body by the vehicle speed from the detection means by the computer. A horizontal vibration damping method for a railway vehicle, characterized by selectively switching and controlling an unload valve for a pressure side and an unload valve for a new side. A cylinder that is opened between the bogie and the vehicle body, a flow path that allows only a flow of the working fluid from the head side chamber of the cylinder to the rod side chamber, a reservoir through the suction valve to the head side chamber of the cylinder, and the head side chamber communicate with the reservoir. And an unload valve for pressure side installed in the flow path, an unload valve for the new side installed in the flow path communicating the rod side chamber with the head side chamber, and a damping force control circuit interposed between the rod side chamber and the reservoir. The damping force control circuit has a fixed contraction portion and a proportional electromagnetic relief valve which is provided in parallel with the fixed contraction portion and controls the relief set pressure continuously from the highest pressure to the lowest pressure in accordance with the increase in the input from the proportional solenoid. The proportional electromagnetic relief valve communicates with the valve case, the inlet port and the return port provided in the valve case, and the inlet port and the return port. A sliding valve seat having an intermittent valve body, a spring for setting the relief pressure for applying a force in the closing direction of the valve body, an adjusting screw body having an adjustment screw for supporting the base of the spring, and an opening direction with respect to the valve body In communication with the return port of the hydraulic chamber while pressing the valve body by the excitation of the solenoid located between the hydraulic chamber formed between the solenoid applying the force and the valve seat and the solenoid and the movable core of the valve body and the solenoid. A damping force value closest to the maximum value generated in the damping force control circuit in accordance with only a signal on the vehicle body side such as a vehicle speed signal from a detection means installed in the vehicle body using a damping damper having a switching valve for communication to the inlet port. Is computed by a computer, and the proportional electronic relief valve is proportionally controlled according to the And detecting the vibration direction of the vehicle body by a computer by means of the vehicle body speed by the detection means, and selectively switching and controlling the unload valve for the pressure side and the unload valve for the new side.