JP2009234516A - Stopper - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a stopper of lightweight and small-sized construction excellent in the economy and capable of exerting the damping force many times. <P>SOLUTION: The stopper S installed between the body B of a railroad vehicle and its bogie W and restricting the displacement of the body G in the horizontal direction sideways relative to the bogie W is equipped with a cylinder 1 fixed to either of the body B and the bogie W, a piston 2 inserted in the cylinder 1 slidably for forming therein 1 a pressure chamber R1 to be filled with liquid, a piston 2 to abut on the other of the body B or the bogie W when the displacement is restricted, a reserver R2 to be in communication with the pressure chamber R1 through a relief passage 3 and a suction passage 4, a relief valve 5 installed on the way of the relief passage 3 to give a resistance to the liquid flow when relieving is made, a check valve 6 installed on the way of the suction passage 4 to admit only the liquid flow directed to the pressure chamber R1 from the reserver R2, and an energizing means 7 to energize the piston 2 toward the other of the body and bogie. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to an improvement in a stopper that is interposed between a vehicle body and a carriage of a railway vehicle and restricts a horizontal and lateral displacement of the vehicle body with respect to the carriage.

  For example, a pin in a bolsterless bogie through which a central pin fixed to the car body is inserted is used as a stopper that is interposed between the car body and the car in this type of railway vehicle and restricts the horizontal and lateral displacement of the car body relative to the car. It is known that an elastic body is provided on the side of the insertion hole, and the elastic body collides with the center pin when the vehicle body is greatly displaced to the left or right with respect to the carriage. While mitigating the impact, further displacement of the vehicle body relative to the carriage is regulated (see, for example, Patent Document 1).

  Such a stopper can slightly attenuate the vibration of the vehicle body relative to the carriage, but when a large external force is applied to the vehicle body due to an earthquake or the like and the vehicle body is vibrated in the left-right direction, the vehicle body effectively acts on the carriage. Cannot expect to attenuate the vibration.

  To solve this problem, a box-shaped holder, a stop plate inserted movably with respect to the holder, an aluminum honeycomb interposed between the holder and the stop plate, and a holder and a stop plate There has been proposed a stopper configured to include a coil spring interposed therebetween and a fuse bolt for fixing the holder to the stop plate.

  In this stopper, when the vehicle body exhibits significant lateral vibration with respect to the carriage and the center pin collides with the stopper, if a force exceeding a predetermined level is applied to the stopper, the fuse bolt breaks and the holder The aluminum honeycomb is compressed and plastically deformed by the displacement of the vehicle body (see, for example, Patent Document 2).

The vibration energy of the vehicle body is absorbed by the plastic deformation of the aluminum honeycomb, and the vehicle body vibration is attenuated. This stopper sufficiently vibrates even if the vehicle body vibrates due to a large input such as an earthquake. Can be attenuated.
JP 2006-151078 A JP 2006-182111 A

  However, the proposed stopper dampens vibrations due to plastic deformation of the aluminum honeycomb and cannot exert damping force after plastic deformation. Therefore, when the vehicle body repeats significant lateral vibration with respect to the carriage, the damping force is no longer present. The vehicle body vibration cannot be suppressed sufficiently.

  In addition, since the proposed stopper cannot exert damping force after plastic deformation of the aluminum honeycomb as described above, the plastic deformation of the aluminum honeycomb is detected when an earthquake occurs or when significant lateral movement of the vehicle body is detected. In addition to the disadvantage of frequent maintenance of the stopper, parts must be replaced, which is economically disadvantageous.

  On the other hand, since the railway vehicle is provided with a damper that attenuates left and right vibration of the vehicle body relative to the carriage, it can be proposed that the damper should perform the function of the stopper. Because the vibration of the vehicle body becomes so great that the above damper can no longer suppress the vibration and the displacement of the carriage with respect to the vehicle body is restricted, and it exhibits a very large damping force compared to the damper. In order to incorporate this stopper function into the damper, there is a risk that the size of the damper and an increase in weight are unavoidable and the mountability on the vehicle is impaired, and the entire system may become extremely expensive.

  Therefore, the present invention was devised in order to improve the above-mentioned problems, and the object of the present invention is to provide a stopper that can exhibit a damping force any number of times, is lightweight, small and excellent in economy. is there.

  In order to achieve the above-described object, the problem-solving means of the present invention includes a stopper that is interposed between a vehicle body and a carriage of a railway vehicle and restricts horizontal displacement of the vehicle body relative to the carriage. A cylinder that is slidably inserted into the cylinder and is filled with liquid in the cylinder, and a piston that collides with the other of the vehicle body or the carriage when displacement is restricted, and a relief flow in the pressure chamber A reservoir communicating with the passage through the suction flow path, a relief valve provided in the middle of the relief flow path to provide resistance to the flow of liquid during relief, and provided in the middle of the suction flow path from the reservoir to the pressure chamber There was provided a check valve that allowed only the flow of the liquid to be directed, and a biasing means that biased the piston toward the other side of the vehicle body or the carriage.

  The stopper of the present invention, unlike a conventional stopper that can only exhibit a damping force only once, can exhibit a damping force repeatedly and continuously, so it is not necessary to frequently perform maintenance of the stopper, and parts can be replaced. Since it is unnecessary, it is economically advantageous.

  In addition, since a single pressure chamber is formed in the cylinder by the piston that abuts the vehicle body or the carriage, the entire cross-sectional area in the cylinder contributes to the generation of the damping force, so that a large damping force can be obtained. Compared with incorporating a stopper function in the damper, it is possible to suppress significant vibration of the body of the vehicle with a light, small and simple structure, without impairing the mountability to the railway vehicle, and greatly attenuating Compared with obtaining an effect, the cost can be reduced and a cost-effective stopper can be realized.

  Therefore, the stopper of the present invention can exhibit a damping force any number of times, is lightweight, small in size and excellent in economy.

  The present invention will be described below based on the embodiments shown in the drawings. FIG. 1 is a cross-sectional view of a stopper according to an embodiment. FIG. 2 is a cross-sectional view of a stopper according to another embodiment.

  As shown in FIG. 1, the stopper S in one embodiment includes a cylinder 1 fixed to a carriage W of a railway vehicle, and a pressure chamber that is slidably inserted into the cylinder 1 and is filled with liquid. Piston 2 forming R1, reservoir R2 communicating with pressure chamber R1 via relief flow path 3 and suction flow path 4, and provided in the middle of relief flow path 3 to provide resistance to the flow of liquid during relief A relief valve 5; a check valve 6 that is provided in the middle of the suction flow path 4 and allows only a liquid flow from the reservoir R2 to the pressure chamber R1; and an urging means that urges the piston 2 toward the vehicle body B. A coil spring 7 is provided, and when the vehicle body B vibrates in the horizontal direction with respect to the carriage W, the piston 2 is brought into contact with the vehicle body B to restrict further displacement of the vehicle body B. Along with the body B It is intended to damp the vibrations to.

  In the following, the cylinder 1 has a cylindrical shape, and the left end of the cylinder 1 in FIG. 1 is closed by an annular guide member 8 that slidably supports the piston 2, and in FIG. The right end is also closed by the bottom member 9.

  The cylinder 1 is housed in a bottomed cylindrical outer cylinder 10 together with the bottom member 9, and a reservoir R <b> 2 is formed by an annular gap between the outer cylinder 10 and the cylinder 1. Further, the guide member 8 described above is fixed to the inner periphery of the open end of the outer cylinder 10, the open end is closed, the reservoir R2 is maintained in a sealed state, and gas and liquid are contained in the reservoir R2. Is filled. Further, a notch 1a is formed at the left end of the cylinder 1 in FIG. 1, and the inside of the cylinder 1 and the reservoir R2 are communicated with each other through the notch 1a.

  The piston 2 includes a bottomed cylindrical main body 2a and a flange 2b that is provided on the outer periphery of the main body 2a and is in sliding contact with the cylinder 1, and the piston 2 is inserted into the cylinder 1 so that the piston 2 A pressure chamber R <b> 1 is formed between the cylinder 2 and the cylinder 1.

  Specifically, the flange 2b includes a piston ring 2c as a bearing on the outer periphery, and is in sliding contact with the cylinder 1 via the piston ring 2c. The outer periphery of the main body 2a is slidably inserted into a cylindrical bearing 8a provided on the inner periphery of the guide member 8, and the piston 2 is guided by the guide member 8 to the cylinder 1 in FIG. It can be displaced in the left-right direction. In addition, the guide member 8 includes an annular seal member 8b slidably contacting the outer periphery of the main body 2a of the piston 2, the outer periphery of the piston 2 is sealed, and the inside of the cylinder 1 is maintained in a sealed body.

  Further, the piston 2 is always urged toward the left in FIG. 1 which is a direction toward the vehicle body B by projecting from the cylinder 1 by a coil spring 7 interposed between the piston 1 and the piston 2. If no force in the direction of pushing into the cylinder 1 is applied to the cylinder 1, the piston 2 is maintained in the most extended state in which further protrusion with respect to the cylinder 1 is restricted by the collision of the flange portion 2 b with the guide member 8. .

  1 is provided with a chamfer 2d, and the piston 2 is in contact with the cylinder 1 at the left end in FIG. 1 of the flange 2b against the right end of the guide member 8 in FIG. However, the notch 1a provided on the side of the cylinder 1 is not blocked by the chamfer 2d.

  An elastic body 11 such as rubber or synthetic resin is fixed to the left end of the piston 2 in FIG. 1, and the elastic body 11 precedes the piston 2 when the vehicle body B is greatly displaced with respect to the carriage W. It collides with the vehicle body B so as to reduce the impact caused by the collision between the vehicle body B and the carriage W.

  Subsequently, the bottom member 9 is provided with a relief flow path 3 that communicates the pressure chamber R1 and the reservoir R2, and a suction flow path 4 that similarly communicates the pressure chamber R1 and the reservoir R2. A relief valve 5 arranged in the middle and a check valve 6 arranged in the middle of the suction flow path 4 are also provided in the bottom member 9 in the same manner.

  The relief valve 5 does not allow the flow of liquid from the reservoir R2 to the pressure chamber R1, and opens the relief channel 3 when the pressure in the pressure chamber R1 reaches a predetermined relief pressure. It also functions as a damping valve that provides resistance to the flow of liquid passing therethrough. In contrast to the relief valve 5, the other check valve 6 prevents the flow of liquid from the pressure chamber R1 to the reservoir R2, and allows only the liquid flow from the reservoir R2 to the pressure chamber R1. .

  In the case of this embodiment, the stopper S configured in this way is configured to fix the cylinder 1 to the carriage W via the outer cylinder 10, and specifically, for example, a center pin of the carriage W It is attached to the inner peripheral side of the insertion hole. On the other hand, for example, the piston 2 is opposed to a center pin as a part of the vehicle body B extending to the vehicle body B with a predetermined interval L, and the vehicle body B is in a neutral position with respect to the carriage W. The center pin is brought into contact with the piston 2 via the elastic body 11 when displaced by a predetermined distance L or more. Although the stopper S is arranged only on the right side of the center pin in the drawing, it is actually installed on the left inner periphery of the center pin insertion hole in the carriage W as a center. Even if the vehicle is displaced from the neutral position to the left side with respect to the carriage W by a predetermined distance L or more, the displacement is restricted by a left stopper S (not shown).

  Conversely, the cylinder 1 may be fixed to the vehicle body B, and the piston 2 may be opposed to the carriage W. Further, in order to fix the cylinder 1 to one of the vehicle body B and the cart W, in addition to the case of fixing the cylinder 1 directly to the vehicle body B (cart W), it is indirectly possible through an accessory integrated with the vehicle body B (cart W). In order to make the piston 2 collide with the other of the vehicle body B and the carriage W, similarly, in addition to the case where the piston 2 is abutted directly with the vehicle body B (cart W), the vehicle body B (cart) Indirect abutting via attachments integrated into W) is also included.

  In addition, the position where the stopper S is installed is set between the center pin, which is a part of the vehicle body B, and the center pin insertion hole of the cart W, as well as a portion where the displacement of the cart W of the vehicle body B can be regulated. It may be.

  Next, the operation of the stopper S will be described. When the left and right vibrations act on the vehicle body B and are displaced by a predetermined distance L or more with respect to the carriage W, and the vehicle body B collides with the piston 2, the piston 2 is pushed into the cylinder 1 due to the proximity of the vehicle body B and the cylinder 1. In a state where the pressure in the pressure chamber R1 compressed by the force does not reach the relief pressure of the relief valve 5, the stopper S does not contract and only the compression of the elastic body 11 attenuates the vibration of the vehicle body B, and the vehicle body B and the carriage. Mitigates the impact of W collision.

  On the other hand, when the pressure in the pressure chamber R1 compressed by the force that the vehicle body B pushes the piston 2 into the cylinder 1 reaches the relief pressure of the relief valve 5, the relief valve 5 opens the relief flow path 3. The liquid in the pressure chamber R1 is released while applying resistance to the reservoir R2, and the piston 2 is pushed into the cylinder 1 and applies a damping force in the direction opposite to the vibration direction to the vehicle body B. Therefore, in this state, the stopper S exhibits a damping force while being compressed and suppresses vibration of the vehicle body B with respect to the carriage W. Further, since the piston 2 receives pressure only from the pressure chamber R1 side, the generated damping force of the stopper S is obtained by multiplying the pressure in the pressure chamber R1 by the cross-sectional area in the cylinder. A large damping force can be exhibited by utilizing the entire cross-sectional area. It should be noted that the damping characteristics (the characteristics of the speed of the piston 2 relative to the cylinder 1 and the generated damping force) after the relief valve 5 is opened can be arbitrarily set.

  At this time, since the liquid is supplied from the reservoir R2 to the annular gap generated by separating the flange portion 2b of the piston 2 from the guide member 8 through the notch 1a of the cylinder 1 and the chamfer 2d of the flange portion 2b, Negative pressure is not generated in the annular gap, and movement of the piston 2 is not hindered. In order to prevent a negative pressure from being generated in the annular gap, a chamfer 2d may be provided, and a notch or a stepped portion may be provided on at least a portion of the shoulder of the flange portion 2b facing the notch 1a. Further, instead of providing the cylinder 1 or the piston 2 with the notch 1a or the chamfer 2d, the guide member 8 may be provided with a passage or a notch for communicating the annular gap and the reservoir R2.

  Thereafter, when the vibration direction of the vehicle body B with respect to the carriage W is reversed and the vehicle body B is separated from the piston 2, the piston 2 returns to the position where it protrudes from the cylinder 1 by the urging force of the coil spring 7. At this time, since the pressure chamber R1 is depressurized by the volume expansion, the check valve 6 is opened, and the liquid is supplied from the reservoir R2 to the pressure chamber R1 through the suction flow path 4, and the piston 2 quickly returns to the original state. It can return to the position. Since the liquid escapes from the annular gap between the flange 2b of the piston 2 and the guide member 8 to the reservoir R2 through the notch 1a and the chamfer 2d, the return operation of the piston 2 is not hindered.

  When the piston 2 returns to the original position, the stopper S exhibits a compression action and exhibits a damping force against the collision of the vehicle body B again, and effectively suppresses repeated vehicle body vibrations. be able to.

  In other words, unlike the conventional stopper that can exhibit the damping force only once, the stopper S can exhibit the damping force repeatedly and continuously. Since no replacement is necessary, it is economically advantageous.

  In addition, since the piston 2 forms a single pressure chamber R1 in the cylinder 1, the entire cross-sectional area in the cylinder can contribute to the generation of the damping force and a large damping force can be obtained. Compared with incorporating functions, it is possible to suppress significant vibration of the vehicle body B with respect to the carriage W with a light, small and simple configuration, without impairing the mounting property on the railway vehicle, and providing a great damping effect. The cost is lower than that obtained, and the cost-effective stopper S can be realized.

  Therefore, the stopper S of the present invention can exhibit a damping force any number of times, is lightweight, small and excellent in economy.

  Furthermore, since the piston 2 is configured to include a bottomed cylindrical main body 2a and a flange portion 2b that is provided on the outer periphery of the main body 2a and is in sliding contact with the cylinder 1, the piston 2 is lightweight. In this case, it can contribute to further weight reduction.

  In the above, the annular gap between the flange portion 2b of the piston 2 and the guide member 8 is also hermetically sealed, so that a notch 1a and a chamfer 2d are provided to communicate with the reservoir R2. If the annular gap may be opened to the atmosphere, and the guide of the piston 2 can be realized by the cylinder 1 and the flange portion 2b, the guide member 8 can be used to avoid the formation of the annular gap. The guide member 8 may be made to function only as a retaining stopper that abuts against the flange 2b of the piston 2.

  Further, since the urging means is provided to exhibit the function of returning the piston 2 to the position before the stopper S is compressed, the urging means is applied to the coil spring 7 if this function can be exhibited. If the reservoir R2 acting as a gas spring is an urging means and the piston 2 can be returned to the position before the stopper S is compressed by the pressure of the gas sealed in the reservoir R2, the coil spring is not limited. 7 can also be omitted.

  Next, a stopper S ′ in another embodiment shown in FIG. 2 will be described. The stopper S ′ in the other embodiment is different from the stopper S in the embodiment in that a reservoir R2 is provided in the piston 13 and a relief channel 3 and a suction channel 4 are provided in the piston 13. It is.

  In the description of the stopper S 'in the other embodiment, the description of the same part as the stopper S of the one embodiment is repeated, and therefore the detailed description is omitted only by attaching the same reference numerals.

  Hereinafter, the above-described different points will be described in detail. The piston 13 includes a disk-like base portion 13a that is in sliding contact with the inner periphery of the bottomed cylindrical cylinder 12, and a shaft portion 13b that has a hollow portion 13c that rises from the base portion 13a. A pressure chamber R1 is formed between the base portion 13a and the cylinder 12.

  The shaft portion 13 b is slidably supported by an annular guide member 8 that closes the open end of the cylinder 12, and a free piston 14 is slidably inserted into the hollow portion 13 c, and is hollowed by the free piston 14. The inside of the part 13c is partitioned into a liquid chamber L filled with liquid and an air chamber G filled with gas.

  The liquid chamber L is communicated with the pressure chamber R1 by the relief flow path 3 and the suction flow path 4 provided in the base portion 13a, and a liquid flow from the liquid chamber L toward the pressure chamber R1 is in the middle of the relief flow path 3. Is provided, and when the pressure in the pressure chamber R1 reaches a predetermined relief pressure, a relief valve 5 is provided that opens the relief flow path 3 and provides resistance to the flow of liquid from the pressure chamber R1 to the liquid chamber L. The other suction flow path 4 is provided with a check valve 6 that allows only the flow of liquid from the liquid chamber L toward the pressure chamber R1.

  That is, in the stopper S ′ of the other embodiment, since the relief channel 3, the suction channel 4, the relief valve 5 and the check valve 6 are all provided in the base portion 13a of the piston 13, the bottom member 9 is not required, and the volume of the pressure chamber R1, which fluctuates due to the advance and retreat of the piston 13 with respect to the cylinder 12, is compensated by the volume change of the air chamber G. In this embodiment, the reservoir R2 is Since the liquid chamber L and the air chamber G are configured and installed in the piston 13, the outer cylinder 10 becomes unnecessary.

  Although not shown, even if the annular gap between the base portion 13a of the piston 13 and the guide member 8 is communicated with the liquid chamber L and the piston 13 is displaced in the direction in which the piston 13 protrudes with respect to the cylinder 12, A negative pressure may be generated in the gap, and the annular gap may be opened to the atmosphere.

  Even in the stopper S ′ according to another embodiment configured as described above, when the pressure in the pressure chamber R1 compressed by the force of pushing the piston 13 into the cylinder 12 reaches the relief pressure of the relief valve 5, The relief valve 5 opens the relief flow path 3 to allow the liquid in the pressure chamber R1 to escape while applying resistance to the liquid chamber L of the reservoir R2, and the piston 13 is pushed into the cylinder 12 and reverse to the vibration direction. The damping force is applied. That is, even in the stopper S ′, the damping force can be exerted while performing the compression operation to suppress the vibration of the vehicle body B with respect to the carriage W, and the piston 13 receives pressure only from the pressure chamber R1 side. Therefore, the generated damping force of the stopper S is obtained by multiplying the pressure in the pressure chamber R1 by the cross-sectional area in the cylinder, and exhibits a large damping force by utilizing the entire cross-sectional area in the cylinder. Can do. In this stopper S ′, the pressure chamber R1 and the liquid chamber L are pressurized by the gas pressure in the air chamber L, and the urging force in the direction protruding from the cylinder 12 always acts on the piston 13, and this is urged. Even when compressed as a means, the piston 13 can return to the original position where it protrudes from the cylinder 12 most.

  Therefore, even in this stopper S ′, unlike the conventional stopper that can exhibit the damping force only once, the damping force can be exhibited repeatedly and continuously, so that the maintenance of the stopper S is not frequently performed. Often, replacement of parts is unnecessary, which is economically advantageous.

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

It is sectional drawing of the stopper in one Embodiment. It is sectional drawing of the stopper in other embodiment.

Explanation of symbols

1, 12 Cylinder 1a Notch 2 in cylinder 2 13 Piston 2a Piston body 2b Piston collar 2c Piston piston ring 2d Piston chamfer 3 Relief flow path 4 Suction flow path 5 Relief valve 6 Check valve 7 Energizing means Coil spring 8 Guide member 8a Bearing 8b in guide member Seal member 9 in guide member Bottom member 10 Outer cylinder 11 Elastic body 13a Base portion 13b in piston Shaft portion 13c in piston Free piston B Car body G Air chamber L Liquid chamber R1 Pressure chamber R2 Reservoir S, S 'Stopper W Cart

Claims (3)

A stopper that is interposed between the body of the railway vehicle and the carriage and restricts horizontal displacement of the body relative to the carriage. A cylinder that is fixed to one of the body or the carriage, and is slidably inserted into the cylinder. A pressure chamber filled with liquid in the cylinder and a piston that abuts against the other of the vehicle body or the carriage when displacement is restricted, a reservoir communicated with the pressure chamber via a relief flow channel and a suction flow channel, a relief flow A relief valve that is provided in the middle of the path to provide resistance to the flow of liquid during relief, a check valve that is provided in the middle of the suction flow path and that allows only the flow of liquid from the reservoir to the pressure chamber, A stopper comprising biasing means for biasing toward the other side of the carriage. The stopper according to claim 1, wherein an elastic body facing the other of the vehicle body or the carriage is provided at the tip of the piston. 3. The stopper according to claim 1, wherein the piston includes a bottomed cylindrical main body and a flange provided on the outer periphery of the main body and in sliding contact with the cylinder.

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