JP2011213218A - Journal box support device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a journal box support device which can highly maintain a bend passing performance when a steering instruction in a desired bending direction is inputted, and can achieve a stable bend passing performance by suppressing an increase of a side pressure even when a reversed steering instruction is inputted.SOLUTION: The journal box support device includes a chassis side member 70 having a cylinder part 71, a journal box side member 90 having a rod 91, a hydraulic pressure applying means 100 for applying a hydraulic pressure to a first cylinder chamber 71A and a second cylinder chamber 71B of the cylinder part 71 by a steering instruction, a first piston 76 arranged in the first cylinder chamber 71A for pressing the rod 91 to the chassis frame side when the hydraulic pressure is not applied so that the pressing of the rod 91 is canceled under the hydraulic pressure, a second piston 80 arranged in the second cylinder chamber 71B for pressing the rod 91 to the journal box side under the hydraulic pressure, and a valve part 93 for allowing the application of the hydraulic pressure into the second cylinder chamber 71B only when the rod 91 is displaced toward the journal box side by an external force.

Description

  The present invention relates to an axle box support device for a railway vehicle carriage that supports the vehicle body of the railway vehicle and travels on the rail.

When the railway vehicle passes through a curve, a portion with a large wheel diameter rotates on the rail on the outer gauge side wheel, and a portion with a small wheel diameter rotates on the rail on the inner gauge side wheel. The difference compensates for the rail length difference between the outer and inner gauges.
However, during such a curved run, the rolling direction of the wheels does not coincide with the contact direction of the curve. For this reason, an angle called an attack angle is generated between the wheel tread surface and the wheel tread contact surface of the rail, and a lateral pressure is generated between the wheel and the rail due to the stress caused by this and the centrifugal force of the vehicle.

  When the lateral pressure as described above is generated, the rail is pushed and the wear of the rail and the wheel is accelerated, so that the maintenance cost is increased, and further, a creaking sound between the wheel and the rail is generated. In addition, the lateral pressure becomes more pronounced as the speed at the time of curve traveling increases, while improvement of the curve traveling speed is desired in order to shorten the arrival time to the destination.

  In order to cope with this, in Patent Document 1, a coupling means is configured by connecting an axle box side member coupled to the axle box side and a carriage side member coupled to the carriage side so as to be capable of relative displacement in the vehicle traveling direction. Has been disclosed. This connecting means increases the internal pressure of the air spring when passing through the vehicle curve, and a return spring that biases in a direction to shorten the distance between the axle box side member and the cart side member, an air spring that biases in the direction of extension Control means is provided.

  According to this axle box support device, when the vehicle is traveling in a straight line, the axle box side member and the carriage side member come closer to each other by the return spring, and the rigidity against the tensile load is increased, thereby improving the running stability. On the other hand, when the vehicle is traveling on a curve, a steering command for increasing the internal pressure of the air spring on the outer gauge side is input from the control means. Thereby, the distance between the axle box side member and the cart side member is separated, and the wheel shaft can be steered. Further, at this time, since the rigidity of the connecting means is reduced, the connecting means is more easily extended, so that the wheel shaft can be steered more smoothly and the curve passing performance can be improved.

JP 2008-247173 A

  In the prior art, the curve passing performance in the bending direction corresponding to the steering command is improved by the steering command of either the right turn or the left turn by the control device. However, if a reverse steering command is input, that is, if a left turn steering command is made despite a right turn, or if a right turn steering command is made despite a left turn, the attack angle There is a problem that the lateral pressure increases due to an increase in the pressure.

  Here, for example, if the maximum separation distance between the axle box side member and the carriage side member is reduced to some extent by limiting the amount of increase in the internal pressure of the air spring, the increase in lateral pressure during reverse steering is also reduced accordingly. It is thought that it can be made. However, this is not preferable because the curve passing performance when the steering command is normally input is deteriorated.

  The present invention has been made in view of such problems, and can maintain a high curve passing performance when a steering command in a desired bending direction is input, and a reverse steering command is input. It is an object of the present invention to provide an axle box support device that can suppress an increase in lateral pressure and realize a stable curve passing performance even at the time.

In order to solve the above problems, the following means are proposed.
That is, the axle box support device according to the present invention is configured such that the axle boxes provided at both ends of the front axle and the rear axle of the railway vehicle bogie are connected to the bogie frame of the bogie by connecting means extending in the longitudinal direction of the vehicle. And the connecting means is attached to the carriage frame, and is attached to the axle box and inserted into the cylinder part. A shaft box side member having a rod displaceable toward the side, a fluid pressure supply means for supplying fluid pressure to the first cylinder chamber and the second cylinder chamber of the cylinder portion by a steering command, and the first A first piston is provided in the cylinder chamber and presses the rod toward the carriage frame when the fluid pressure is not supplied, and is disposed in the second cylinder chamber, and the pressure of the rod is canceled by the fluid pressure. A second piston that presses the rod toward the axle box by the fluid pressure, and allows the fluid pressure to be supplied into the second cylinder chamber only when the rod is displaced toward the axle box by an external force. And valve means.

Here, when traveling along a curve, the external force F _out toward the front in the vehicle traveling direction, that is, the external force (tensile load) F _out in the direction in which the front wheel is separated from the cart side member is the rail. Given by. On the other hand, an external force (compression load) F _in toward the rear in the vehicle traveling direction, that is, an external force F _in for bringing the front wheel closer to the carriage side member is applied to the front wheel on the inner rail side from the rail.

  In the axle box support device of the present invention, the rigidity with respect to the tensile load is ensured by the first piston in the first cylinder chamber pressing the rod against the cart frame side during linear travel without input of a steering command. High running stability can be realized.

Then, when a normal steering command is input when passing the curve, supply of fluid pressure by the fluid pressure supply means is started in the outer side axle box support device. At this time, fluid pressure is supplied to the first cylinder chamber in the cylinder portion, but supply of the fluid pressure is prohibited to the second cylinder chamber by the valve means. As a result, the pressure on the rod of the first piston is canceled in the first cylinder chamber, and the restriction of the rod by the first piston is released. As a result, the rod becomes displaceable to the axle box side. At this time, when the external force F _out of the outer rail side during cornering the axle box support device of the outer rail side is given, rod restraint by the first piston is released displaced in the axial box side. Then, in conjunction with this, supply of fluid pressure into the second cylinder chamber by the valve means is allowed, and the second piston in the second cylinder chamber presses the rod toward the axle box side by the fluid pressure. Thereby, the rod can be displaced further toward the axle box side. That is, since the connecting means can be arbitrarily extended by displacing the rod in accordance with the magnitude of the fluid pressure to be supplied, the curve passing performance can be improved.

On the other hand, when a reverse steering command is input when passing the curve due to some trouble, supply of fluid pressure by the fluid pressure supply means is started in the inner side axle box support device. At this time, the fluid pressure is supplied only to the first cylinder chamber of the cylinder portion, so that the restriction of the rod by the first piston is released, and the rod can be displaced to the axle box side. At this time, the axle box support device of the inner rail side, since an external force F _in the inner during cornering rail side is provided, the rod is never displaced in the axial box side. Furthermore, since supply of fluid pressure into the second cylinder chamber by the valve means is not permitted, the second piston does not press the axle box side member. Accordingly, since the rod does not displace to the axle box side, the contraction state of the connecting means can be maintained, and an increase in lateral pressure due to the extension of the connecting means despite the inner rail side is prevented. be able to.

  Further, in the axle box support device according to the present invention, the valve means is provided at an end portion of the rod on the cart frame side and closes the fluid pressure supply port into the second cylinder chamber, It is preferable that the stopper part opens the supply port only when the rod is displaced by an external force.

Thus, the rod by an external force F _out given to the front wheel of the curve outside during cornering only when displaced in the axial box side, so that the pressing force of the second piston with respect to the rod is provided. Therefore, it is possible to prevent the rod from being displaced during reverse steering, and when the normal steering command is input, it is possible to reliably extend the connecting means on the outer gauge side to improve the curve passing performance. It becomes possible.

  Further, in the axle box support device according to the present invention, the magnitude of the fluid pressure received by the stopper portion that closes the supply port toward the axle box side is such that the rod is the carriage in the first cylinder chamber. It is preferable to be configured to be smaller than the magnitude of the fluid pressure received toward the frame side.

Thus, in the case the magnitude of the fluid pressure supplied to the first cylinder chamber and a second cylinder chamber are the same, the displacement of the rod by the fluid pressure in a state in which external force F _out of the outer rail side does not act Can be banned. As a result, even when a steering command is erroneously input during straight traveling or when a reverse steering command is input during curved traveling, the contraction state of the connecting means can be maintained, and the unintended expansion of the connecting means can be maintained. Therefore, it is possible to reliably prevent a decrease in running stability and an increase in pressure due to.

  Further, in the axle box support device according to the present invention, the valve means allows the supply of the fluid pressure into the second cylinder chamber in conjunction with the rod being displaced toward the axle box side by an external force. It may be a solenoid valve.

Thus the same, when running on a curve rod by an external force F _out given to the front wheel of the outer rail side only when displaced in the axial box side, it is possible to impart a pressing force by the second piston with respect to the rod . Therefore, it is possible to prevent the rod from being displaced during reverse steering, and when the normal steering command is input, the connecting means on the outer gauge side is reliably extended to improve the curve passing performance. Is possible.

According to the axle box support device of the present invention, when fluid pressure is supplied according to a steering command, the rod can be displaced to the axle box side, and further, when the rod is displaced to the axle box side by the external force _Fout . By adopting a configuration in which a pressing force toward the axle box side due to only the fluid pressure is applied to the rod, a reverse steering command is issued while maintaining a high curve passing performance when a steering command in a desired bending direction is input. Even when it is input, it is possible to suppress the increase in lateral pressure and realize a stable curve passing performance.

It is a side view of the bogie for rail vehicles provided with the axle box support device concerning a 1st embodiment. It is a longitudinal cross-sectional view of the connection means in the axle box support apparatus which concerns on 1st Embodiment. It is a top view explaining the external force given to each wheel from a rail at the time of curve running. It is a schematic diagram explaining the outline | summary of the connection means of the axle-box support apparatus of 1st Embodiment. It is a schematic diagram explaining operation | movement of the connection means of the axle box support apparatus of 1st Embodiment. It is a schematic diagram explaining operation | movement of the connection means of the axle box support apparatus of 1st Embodiment. It is a schematic diagram explaining operation | movement of the connection means of the axle box support apparatus of 1st Embodiment. It is a schematic diagram explaining operation | movement of the connection means of the axle box support apparatus of 1st Embodiment. It is a longitudinal cross-sectional view of the connection means in the axle box support apparatus which concerns on 2nd Embodiment. It is a schematic diagram explaining the outline | summary of the connection means of the axle box support apparatus of 2nd Embodiment.

Hereinafter, a first embodiment of an axle box support device according to the present invention will be described in detail with reference to the drawings.
FIG. 1 is a side view of a railcar bogie equipped with an axle box support device according to the embodiment, and FIG. 2 is a side sectional view of the axle box support device according to the embodiment.
In the following description, the rail longitudinal direction (vehicle traveling direction) is the front-rear direction, the direction perpendicular to the rail longitudinal direction on the track surface is the left-right direction (vehicle width direction), and the track A vertical direction perpendicular to the surface is referred to as an up-down direction.

  As shown in FIG. 1, the carriage 1 is schematically configured by a carriage frame 10, a carriage air spring 20, a wheel shaft 30, a shaft box 40, and a shaft box support device 50.

  The bogie frame 10 is a structural member serving as a base of the bogie 1, and includes a pair of left and right side beams, a side beam that connects these side beams to the center, and the like. A vehicle body (not shown) is mounted on the vehicle frame 10 via a vehicle body support device such as a vehicle air spring 20 and a traction device.

  The carriage air spring 20 is provided between the carriage frame 10 and the vehicle body and elastically supports the vehicle body. For example, a pair of carriage air springs 20 are provided on the left and right sides of the carriage 1 and are fixedly supported on upper portions of left and right side beams of the carriage frame 10.

The wheel shaft 30 is assembled by press-fitting two substantially disc-shaped wheels 31 into an axle 32, and a pair is provided at the front and rear portions of the carriage 1 so that the axles 32 are parallel to each other. Yes.
The axle box 40 is provided at both ends of the axle 32 of the wheel shaft 30 and supports the wheel shaft 30 so as to be rotatable. The bearing supports the axle 32 so as to be rotatable about its axis, and the bearing. The housing is configured to include a shaft box body that accommodates and a lubrication device.

  The axle box support device 50 is a device that positions and elastically supports the axle box 40 with respect to the carriage frame 10, and a total of four are provided corresponding to each wheel 31. The shaft box support device 50 includes a shaft spring 51, a damper 52, and a connecting means 60. In this embodiment, a monolink type is adopted as the connecting means 60.

The shaft spring 51 is provided across the upper part of the axle box 40 and the lower part of the carriage frame 10 and supports a load in the vertical direction.
The damper 52 is provided between the side portion of the axle box 40 and the carriage frame 10, and generates a damping force and vibrates when the axle box 40 is displaced in the vertical direction with respect to the carriage frame 10. It is to reduce.

  The connecting means 60 is provided in the front-rear direction between the carriage frame 10 and the axle box 40, and both ends thereof are swingably connected to the carriage frame 10 and the axle box 40 by pin joints. ing. The connection part 11 with the connection means 60 in the cart frame 10 is disposed at a position from the substantially central part in the front-rear direction of the cart frame 10 with respect to the axle box 40. One end of the connecting means 60 is connected to the connecting portion 11, and the other end is connected to the connecting portion 41 of the axle box 40.

  As shown in detail in FIG. 2, the connecting means 60 is connected to the carriage frame 10 side and the carriage side member 70 is connected to the axle box 40 side and moves relative to the carriage side member 70 in the front-rear direction. A shaft box side member 90 and a fluid pressure supply means 100 are provided.

  The carriage side member 70 includes a cylinder portion 71 having a first cylinder chamber 71A and a second cylinder chamber 71B inside. The cylinder portion 71 is open to the axle box 40 side (left side in FIG. 2) and has a box body 72 having a bottomed box shape with the bottom 72a facing the cart frame 10 side (right side in FIG. 2). A lid 73 that closes the opening on the axle box 40 side, and an intermediate plate 74 that is provided so as to bisect the internal space formed by the box 72 and the lid 73 in the front-rear direction. Yes. Of the internal spaces, the space on the axle box 40 side defined by the intermediate plate 74 is a first cylinder chamber 71A, and the space on the cart frame 10 side is a second cylinder chamber 71B.

  The lid 73 and the intermediate plate 74 are formed with substantially circular through holes 73a and 74a formed along the central axis O extending in the front-rear direction. The inner diameter dimension of the through hole 73a of the lid 73 is substantially the same as the outer diameter dimension of the axle box side small diameter portion 91a of the rod 91 described later. Further, the inner diameter dimension of the through hole 74a of the intermediate plate 74 is formed to be slightly larger than the inner diameter dimension of the through hole 73a of the lid 73, and has a diameter substantially the same as the outer diameter dimension of the large diameter portion 91b of the rod 91 described later. Has been.

  A bush holding portion 75 is formed on the surface of the cylinder portion 71 facing the cart frame 10 side, that is, the surface of the bottom 72a of the box 72 facing the cart frame 10 side so as to protrude from the surface, A through hole 75 a is formed on the side surface of the bush holding portion 75 in a direction perpendicular to the central axis O on the raceway surface, that is, in a direction parallel to the extending direction of the axle 32. A bogie frame-side bush (not shown) that elastically supports the bogie frame 10 with respect to the bush holding portion 75 is press-fitted into the through hole 75 a, whereby the bogie-side member 70 is connected to the bogie frame 10. It is connected to the part 11.

  A first piston 76 is provided in the first cylinder chamber 71A. The first piston 76 is slidably arranged in the front-rear direction so as to divide the first cylinder chamber 71A into two in the front-rear direction, and has a through hole 76a formed along the central axis O. I have. The inner diameter dimension of the through hole 76a is set to be substantially the same as the inner diameter dimension of the through hole 73a of the lid body 73 described above, that is, the outer diameter dimension of the axle box side small diameter portion 91a of the rod 91 is substantially the same. The diameter is set. Further, the surface of the first piston 76 facing the carriage frame 10 is a flat surface perpendicular to the central axis O, and is a contact surface that can contact the intermediate plate 74 and the shaft box side step portion 91d of the rod 91. 76b.

  Of the space defined by the first piston 76 in the first cylinder chamber 71A, the space on the axle box 40 side is an urging member accommodating chamber 77, and the space on the carriage frame 10 side is a fluid pressure introducing chamber 78. .

  The urging member accommodating chamber 77 is provided with an urging member 79 that urges the first piston 76 toward the cart frame 10 side. In the present embodiment, a disc spring 79a having a thrust washer 79b on the axle box 40 side and a spring guide 79c on the carriage frame 10 side is employed as the biasing member 79. The urging member 79 having such a configuration is formed with an insertion hole 79d along the central axis O. The inner diameter of the insertion hole 79d is determined by the through holes 73a and 74a of the lid 73 and the intermediate plate 74. Is set to a diameter that is substantially the same as or slightly larger than the outer diameter of the axle box side small diameter portion 91a of the rod 91.

  Further, a first supply port 72 b that opens to the outside of the box 72 is formed in the cylinder portion 71, and the first supply port 72 b has a communication passage 74 b drilled inside the intermediate plate 74. One end is connected. The other end of the communication passage 74b opens into the fluid pressure introducing chamber 78 of the first cylinder chamber 71A, and the opening supplies the fluid pressure into the fluid pressure introducing chamber 81 of the first cylinder chamber 71A. 71a.

  A second piston 80 is provided in the second cylinder chamber 71B. The second piston 80 is slidably arranged in the front-rear direction so as to divide the second cylinder chamber 71B into two in the front-rear direction, and has a through hole 80a formed along the central axis O. I have. The inner diameter dimension of the through hole 80a is set to be approximately the same as the outer diameter dimension of the carriage-side small diameter portion 91c of the rod 91. Further, the surface of the second piston 80 facing the axle box 40 is a flat surface perpendicular to the central axis O, and is a contact surface 80 b that contacts the carriage side step portion 91 e of the rod 91.

  Of the space defined by the second piston 80 in the second cylinder chamber 71 </ b> B, the space on the cart frame 10 side is a fluid pressure introducing chamber 81. The cylinder portion 71 is formed with a second supply port 72c that opens to the outside of the box 72. The second supply port 72c is connected to the bottom 72a of the box 72. One end of the passage 72d is connected. The other end of the communication path 72d opens to the fluid pressure introduction chamber 81 of the second cylinder chamber 71B, and the opening serves as a supply port 71b for supplying fluid pressure to the second cylinder chamber 71B. In the present embodiment, the opening direction of the supply port 71b coincides with the central axis O.

  The axle box side member 90 includes a rod 91 that extends along the central axis O and is inserted into the cylinder portion 71. The end portion of the rod 91 on the shaft box 40 side protrudes to the outside of the cylinder portion 71, and a bush holding portion 92 is connected to the end portion. A through hole 92 a is formed on the side surface of the bush holding portion 92 in a direction perpendicular to the central axis O on the raceway surface, that is, in a direction parallel to the extending direction of the axle 32. A shaft box frame-side bush (not shown) that elastically supports the axle box 40 with respect to the bush holding portion 92 is press-fitted into the through hole 92a, whereby the axle box side member 90 is inserted into the axle box 40. The connection part 41 is connected.

  The portions of the rod 91 that are inserted into the cylinder portion 71 are, in order from the axle box 40 side to the carriage frame 10 side, an axle box side small diameter portion 91a, a large diameter portion 91b, and a carriage side small diameter portion 91c. The large diameter portion 91b is formed so as to be slightly larger in diameter than the axle box small diameter portion 91a and the cart side small diameter portion 91c. A step portion between the large-diameter portion 91b and the shaft box side small diameter portion 91a is a shaft box side step portion 91d having a flat ring shape facing the shaft box 40 side. Further, the step portion between the large diameter portion 91b and the cart side small diameter portion 91c is a cart side step portion 91e having a flat ring shape facing the cart frame 10 side.

In such a state that the rod 91 is inserted into the cylinder portion 71, the carriage-side small diameter portion 91 c passes through the through hole 80 a of the second piston 80, and the large diameter portion 91 b passes through the through hole 74 a of the intermediate plate 74. The shaft box side small diameter portion 91 a passes through the through hole 73 a of the lid 73, the insertion hole 79 d of the biasing member 79, and the through hole 76 a of the first piston 76.
The rod 91 is relatively movable in the direction of the central axis O while ensuring airtightness with the through holes 73a, 74a, and 80a by interposing rod packing, wear rings, scrapers, and the like. Yes.

  The first piston 76 can be brought into contact with the axle box side small diameter portion 91a of the rod 91, and the second piston 80 can be brought into contact with the carriage side small diameter portion 91c.

  Further, the end of the rod 91 on the cart frame 10 side projects in the direction of the central axis O and can close the fluid pressure supply port 71b that opens to the fluid pressure introduction chamber 81 of the second cylinder chamber 71B. A stopper part 93 is provided. The stopper portion 93 closes the supply port 71a by fitting the supply port 71b when the rod 91 is located closest to the carriage frame 10, and from this state, the rod 91 is moved to the axle box 40 side. It is configured to be removed from the supply port 71b when displaced. In the present embodiment, the stopper portion 93 plays a role as valve means for prohibiting or allowing the supply of fluid pressure to the fluid pressure introduction chamber 81 of the second cylinder chamber 71B.

  In the present embodiment, the area of the distal end portion of the stopper portion 93, that is, the area of the pressure receiving surface that receives fluid pressure in the state where the stopper portion 93 closes the supply port 71b is the axis of the rod 91. The area of the box side step portion 91d is smaller.

The fluid pressure supply means 100 sends the fluid pressure to the first supply port 72b and the second supply port 72c, respectively, so that the fluid pressure introduction chamber 78 in the first cylinder chamber 71A and the fluid pressure introduction chamber in the second cylinder chamber 71B. It has a role of supplying fluid pressure to each of 81. This fluid pressure supply means 100 is connected to a control device (not shown), for example, and when a steering command is input when the vehicle passes through a curve, the axle box support device 50 on the outer wheel 31a (see FIG. 3) on the outer gauge side. It operates so that fluid pressure is supplied.
In addition, as a fluid pressure supplied from the fluid pressure supply means 100, an air pressure, a hydraulic pressure, etc. can be employ | adopted suitably.

  Further, in the present embodiment, the first supply port 72b and the second supply port 72c are connected to the same pipe, so that the first supply port 72b and the second supply port 72c always have the same pressure fluid. Pressure will be sent.

Here, FIG. 3 will be described with respect to the external force applied from the rail to each wheel 31 when traveling along a curve.
During the curve running, the front wheel 31a on the outer track side of the four wheels 31a, 31b, 31c, and 31d has an external force F _out forward in the vehicle traveling direction, that is, the front wheel 31a is separated from the cart side member 70. An external force F _{out in the} direction is given from the rail. At this time, the external force F _out acts as a tensile load of the same magnitude also on the axle box side member 90 of the connecting means 60 of the axle box support device 50 of the outer wheel side front wheel 31a.
On the other hand, the front wheels 31b of the inner rail side, the external force F _in the toward the vehicle traveling direction rearward, i.e., an external force F _in the front wheel 31b in a direction to approach the carriage member 70 is provided from the rail. At this time, even for the axle box side member 90 of the connecting means 60 of the axle box support device 50 of the curve inside wheels 31b, the external force F _in acting as similarly sized compression load.

  Based on this, the operation of the axle box support device 50 of the present embodiment will be described with reference to FIGS. 4 to 7 schematically illustrate the connecting means 60 of the axle box support device 50 in FIG. 2, and the components indicated by the reference numerals are as described above.

  First, the operation of the axle box support device 50 during straight running will be described. When the vehicle travels in a straight line without input of a steering command, the connecting means 60 of the axle box support device 50 is in the basic length state shown in FIG. In this state, the first piston 76 in the first cylinder chamber 71 </ b> A presses the axle box side step portion 91 d of the rod 91 by the urging force of the urging member 79. As a result, the rod 91 is located closest to the carriage frame 10, and the stopper portion 93 of the rod 91 is in a state of closing the supply port 71b to the second cylinder chamber 71B.

  In this way, during straight running, the rod 91 is restrained to the basic length state by the pressing of the first piston 76, so that the rigidity against the tensile load acting on the rod 91 is ensured and high restraint stability is realized. can do.

Next, the operation of the axle box support device 50 when a steering command is input will be described.
When the steering command is normally input when passing the curve, the introduction of fluid pressure to the first supply port 72b and the second supply port 72c by the fluid pressure supply means 100 is started in the outer side axle box support device 50. At this time, the fluid pressure is supplied to the fluid pressure introducing chamber 78 of the first cylinder chamber 71A via the communication path 72d. On the other hand, for the fluid pressure introduction chamber 81 of the second cylinder chamber 71B, the stopper plug 93 of the rod 91 closes the supply port 71b to the fluid pressure introduction chamber 81, so that supply of fluid pressure is prohibited. The

  As a result, in the first cylinder chamber 71A, the fluid pressure acts on the contact surface 76b of the first piston 76, so that the first piston 76 resists the urging force of the urging member 79 and the axle box 40 side. (See FIG. 5). That is, when the fluid pressure is supplied, the urging force of the urging member 79 is canceled, and the restriction of the axle box side step portion 91d of the rod 91 by the first piston 76 is released. As a result, the rod 91 becomes displaceable toward the axle box 40 side.

In this case, when an external force acts F _out given in the curve outside the axle box support device 50 during cornering of the curve outside, the external force F _out against the rod 91 which is constrained by the first piston 76 is released However, the rod 91 is displaced to the axle box 40 side (see FIG. 6). Then, in conjunction with this, the stopper part 93 opens the supply port 71b to the second cylinder chamber 71B, and supply of fluid pressure to the fluid pressure introduction chamber 81 of the second cylinder chamber 71B is started.

When fluid pressure acts on the second piston 80, the pressing force due to the fluid pressure also acts on the rod 91 that comes into contact with the second piston 80 via the carriage side step portion 91e. Thus, the pressing force F _P by the second piston is applied to the rod 91 can be further displaced toward the rod 91 to the axle box 40 side (see FIG. 7).
Thus, in addition to the external force F _out, it is possible to displace the rod 91 by the pressing force F _P of the second piston 80 by the fluid pressure supplied to the second cylinder chamber 71B to the axle box 40 side. Thereby, since the front-back direction length of the connection means in the front wheel 31a on the outer track side can be extended, the curve passing performance can be improved.

Next, the operation of the axle box support device 50 in the case of reverse steering will be described.
When a reverse steering command is input when passing a curve due to some problem, supply of fluid pressure by the fluid pressure supply means 100 is started in the inner rail side axle box support device 50. As a result, the fluid pressure is supplied only to the first cylinder chamber 71A of the cylinder portion 71, the restriction of the rod 91 by the first piston 76 is released, and the rod 91 becomes displaceable toward the axle box 40 side ( (See FIG. 6).

Then, the axle box support device 50 of the inner rail side, an external force F _in the inner during cornering rail side acts (see Fig. 8), the well relative to the rod 91 constrained is released by the first piston 76 external force external force F _in is applied. At this time, since the rod 91 is not displaced toward the axle box 40, the stopper portion 93 is maintained in a state where the supply port 71b is closed. Therefore, the supply of fluid pressure into the second cylinder chamber 71B is not permitted, and the second piston 80 does not press the rod 91 toward the axle box 40 side. Thereby, the connection means 60 can be maintained in the basic length state, and an increase in lateral pressure due to the extension of the connection means despite the inner rail side can be prevented.

Thus, according to the axle box support device 50 of the present embodiment, the rod 91 can be displaced to the axle box 40 side by supplying fluid pressure according to the steering command, and further, the rod 91 is moved by the external force _Fout . By adopting a configuration in which the pressing force by the second piston 80 is applied to the rod 91 only when displaced toward the axle box 40 side, while maintaining a high curve passing performance when a steering command in a desired bending direction is input, Even when a reverse steering command is input, a stable curve passing performance can be realized by suppressing an increase in lateral pressure.

As shown in FIG. 8, when the first piston 76 is displaced toward the axle box 40 side, fluid pressure acts on the stopper part 93 so that the stopper part 93 is pressurized toward the axle box 40 side. In addition, the fluid pressure acts on the axle box side step portion 91d, so that the rod 91 receives pressure toward the carriage frame 10 side.
Here, in this embodiment, the area of the pressure receiving surface where the stopper part 93 receives the fluid pressure is smaller than the area of the axle box side step part 91d of the rod 91. Therefore, when fluid pressures in opposite directions act on each of the stopper part 93 and the axle box side step part 91d as described above, a force toward the carriage frame 10 acts on the rod 91 as a whole. Therefore, the rod 91 does not move carelessly due to fluid pressure.

State Accordingly, when the magnitude of the first cylinder chamber 71A and the fluid pressure supplied to the second cylinder chamber 71B as in this embodiment are the same, the external force F _out of the outer rail side does not act Displacement of the rod 91 due to the fluid pressure at can be prohibited. Therefore, the connecting means 60 can be maintained in the basic length state even when a steering command is mistakenly input during straight traveling or when a reverse steering command is input during curved traveling. It is possible to reliably prevent a decrease in running stability and an increase in pressure due to the stretching of the belt.

Next, a second embodiment of the axle box support device according to the present invention will be described with reference to FIGS. FIG. 9 is a longitudinal sectional view of the connecting means in the axle box supporting device according to the second embodiment, and FIG. 10 is a schematic diagram for explaining the outline of the connecting means of the axle box supporting device in the second embodiment.
In FIGS. 9 and 10, the same components as those in FIGS. 2 and 5 are denoted by the same reference numerals, and detailed description thereof is omitted.

  As shown in FIG. 9, in the axle box support device 50 of the second embodiment, the rod 91 is not provided with the stopper portion 93. Instead, the rod 91 is moved from the initial position, that is, the connecting means 60 is provided. Detection means 110 is provided for detecting displacement from a position that becomes the basic length. The fluid pressure supply port 71 b to the fluid pressure introduction chamber 81 of the second cylinder chamber 71 </ b> B opens at a position spaced from the central axis O.

Further, as shown in FIG. 10, an electromagnetic valve 111 is provided in a connection pipe to the second supply port 72 c in the fluid pressure supply means 100. The electromagnetic valve 111 is opened only when the detecting means 110 detects the displacement of the rod 91 toward the axle box 40, and allows supply of fluid pressure to the second supply port 72c, while the rod 91 is in the initial position. In other words, when the connecting means 60 is at the position where the basic length is reached, the closed state is established. That is, in this embodiment, the electromagnetic valve 111 constitutes valve means, and fluid pressure is generated in the second cylinder chamber 71B in conjunction with the rod 91 being displaced _{toward the} axle box 40 side by the external force Fout. It is configured to be supplied.

This also similarly to the first embodiment, the rod 91 by an external force F _out given to the front wheel 31a of the outer rail side during cornering only when the displaced axle box 40 side, the second piston with respect to the rod 91 A pressing force of 80 can be applied. As a result, it is possible to prevent the rod 91 from being displaced during reverse steering, and when the normal steering command is input, the connecting means 60 on the outer gauge side is reliably extended to improve the curve passing performance. It becomes possible to improve.

As mentioned above, although embodiment of this invention was described in detail, unless it deviates from the technical idea of this invention, it is not limited to these, A some design change etc. are possible.
For example, the urging member 79 is not limited to the configuration using the disc spring 79a, but may be configured using other members such as a coil spring, an elastic body such as rubber.

  In the embodiment, the example in which the first cylinder chamber 71A is disposed on the axle box 40 side and the second cylinder chamber 71B is disposed on the carriage frame 10 side has been described. However, the embodiment is not limited thereto, and vice versa. The configuration may be a configuration in which the first cylinder chamber 71A is disposed on the cart frame 10 side and the second cylinder chamber 71B is disposed on the axle box side. In this case, the rod 91 is restrained by the first piston 76 in the first cylinder chamber 71A on the carriage frame 10 side, and the rod 91 is moved to the axle box 40 side by the second piston 80 in the second cylinder chamber 71B on the axle box 40 side. Will be pressed.

1 Bogie 10 Bogie Frame 30 Wheel Shaft 31 Wheel 40 Shaft Box 50 Shaft Box Support Device 60 Connecting Means 70 Bogie Side Member 71 Cylinder Unit 71a Supply Port 71b Supply Port 71A First Cylinder Chamber 71B Second Cylinder Chamber 74 Intermediate Plate 76 First Piston 77 Energizing member accommodating chamber 78 Fluid pressure introducing chamber 79 Energizing member 79a Belleville spring 80 Second piston 81 Fluid pressure introducing chamber 90 Shaft box side member 91 Rod 91a Shaft box side small diameter portion 91b Large diameter portion 91c Dolly side small diameter portion 91d Shaft box side step 91e Bogie side step 93 Stopping part (valve means)
100 Fluid pressure supply means 110 Detection means 111 Solenoid valve (valve means)

Claims (4)

An axle box support device that supports axle boxes provided at both ends of the axles of the front and rear wheels of a railway vehicle carriage with respect to the carriage frame of the carriage by connecting means extending in the longitudinal direction of the vehicle,
The connecting means includes
A carriage side member attached to the carriage frame and having a cylinder part;
An axle box side member having a rod attached to the axle box and inserted into the cylinder portion and displaceable toward the axle box side;
Fluid pressure supply means for supplying fluid pressure to the first cylinder chamber and the second cylinder chamber of the cylinder portion by a steering command;
A first piston that is provided in the first cylinder chamber, presses the rod toward the carriage frame when the fluid pressure is not supplied, and cancels the pressing of the rod by the fluid pressure;
A second piston provided in the second cylinder chamber and pressing the rod toward the axle box by the fluid pressure;
A shaft box support device, comprising: valve means that permits supply of the fluid pressure into the second cylinder chamber only when the rod is displaced toward the shaft box side by an external force. The valve means includes
A stopper provided at an end of the rod on the cart frame side, which closes the fluid pressure supply port into the second cylinder chamber and opens the supply port only when the rod is displaced by an external force. The axle box supporting device according to claim 1, wherein the axle box supporting device is a portion.   The magnitude of the fluid pressure that the stopper portion that closes the supply port receives toward the axle box side is greater than the magnitude of the fluid pressure that the rod receives toward the carriage frame side in the first cylinder chamber. The axle box supporting device according to claim 2, which is configured to be smaller. The valve means includes
2. The axle box according to claim 1, wherein the rod box is an electromagnetic valve that allows supply of the fluid pressure into the second cylinder chamber in conjunction with displacement of the rod toward the axle box side by an external force. Support device.

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