JP5254058B2 - Shaft box support device - Google Patents

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 wheel does not coincide with the contact direction of the curved line, so that an angle called an attack angle occurs between the wheel flange and the wheel flange contact surface of the rail. 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 progress of wear increases, so that the maintenance cost is increased, and further, a squeak noise 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, Patent Document 1 proposes a wheel steering device for a railway vehicle in which a moving device such as a cylinder controlled by a control device mounted on the vehicle moves the axle box forward or backward in the vehicle traveling direction. ing.
In this device, when the vehicle is traveling in a curved line, a steering command for extending the distance between the front wheels and the rear wheels is input to the outer rail-side axle box moving device, and the inner-rail side axle box moving device receives the front wheel. -A steering command for shortening the distance between the rear wheels is input. As a result, the turning direction of the wheel approaches the tangential direction of the curve, and the lateral pressure can be reduced.

Further, in Patent Literature 2, a shaft box side member connected to the shaft box side and a cart side member connected to the cart side are connected so as to be relatively displaceable in the vehicle traveling direction to constitute a coupling means, and the shaft Control means for providing a return spring for biasing in a direction for shortening the distance between the box side member and the carriage side member and an air spring for biasing in a direction for extending, and further increasing the internal pressure of the air spring when passing through the curve of the vehicle An axle box support device provided with the above has been proposed.
According to this axle box support device, when the vehicle travels in a straight line, the axle box side member and the carriage side member approach each other by the return spring, and the rigidity against the tensile load increases, thereby improving running stability. In addition, when the vehicle is traveling in a curved line, a steering command for increasing the internal pressure of the air spring on the outer gauge side is input from the control means, so that the distance between the axle box side member and the carriage side member is increased and the wheel shaft is steered. It can be performed. Further, at this time, since the rigidity of the connecting means is reduced, the connecting means is more easily extended. Therefore, the wheel shaft can be steered more smoothly, and the curve passing performance can be improved.

Japanese Patent Laid-Open No. 1-132463 JP 2008-247173 A

  By the way, in the above conventional technique, the curve passing performance in the bending direction corresponding to these steering commands 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.

  The present invention has been made in view of such problems, and even when a reverse steering command is input, an increase in lateral pressure can be suppressed and stable curve passing performance can be realized. An object is to provide a shaft box support device.

の関係が成り立つように、前輪側における外軌側及び内軌側のそれぞれの前記空気バネに供給する前記内圧を制限し、前記空気バネによる伸張力Ｆｐが後輪側に比べて前輪側において小さくなるように、前記空気バネに前記内圧を供給する、ことを特徴とする。 In order to solve the above problems, the following means are proposed.
In other words, the axle box support device according to the present invention provides a carriage frame of the carriage by connecting means extending along the traveling direction of the axle boxes provided at both ends of the axles of the front and rear wheels of the railway vehicle carriage. And the connecting means is attached to the axle box side member attached to the axle box and the bogie frame, and the vehicle travels relative to the axle box side member. A cart-side member connected to be capable of relative displacement in a direction, and a compression force Fs provided between the axle box-side member and the cart-side member and causing the axle box-side member and the cart-side member to approach each other. A return spring, an air spring that is provided between the axle box side member and the carriage side member and generates an extension force Fp that separates the axle box side member and the carriage side member according to the supplied internal pressure; , At least when the vehicle is traveling in a curved line An air spring control means for supplying a predetermined internal pressure to the air spring to increase the extension force Fp of the air spring, and the air spring control means receives the front wheel traveling on the inner track side from the rail in the vehicle traveling direction For external force Fin along

So that the internal pressure supplied to the air springs on the outer race side and the inner race side on the front wheel side is limited, and the extension force Fp by the air spring is smaller on the front wheel side than on the rear wheel side. As described above, the internal pressure is supplied to the air spring .

During the time of cornering, to the front of the outer rail side, the external force F _out of toward the vehicle forward traveling _direction, i.e., the external force F _out in the direction to separate the front wheel from the carriage member is provided from the rail . On the other hand, an external force F _in toward the rear in the vehicle traveling direction, that is, an external force F _in causing the front wheel to approach the carriage side member is applied to the front wheel on the inner track side from the rail.
In the support box support device of the present invention, the extension force F _p of the air spring on the outer track side and the inner track side on the front wheel side is received by the compression force F _s by the return spring and the front wheel on the inner track side from the rail. to be equal to or less than the sum of the external force F _in, since the internal pressure supplied to each of the air springs is limited, even if the command for reverse steering has been input connecting means of the front wheel side the compression force It will not stretch against it. Therefore, it is possible to prevent the occurrence of lateral pressure in the case of reverse steering.

When the vehicle is traveling in a curved line, as described above, the front wheel on the outer track side is given an external force F _out forward in the vehicle traveling direction. Therefore, in front of the curve outside it can be easily stretched to reduce the attack angle by receiving support stretching force F _p with small the external force F _out by the air spring.
In light of this, in the axle box support device of the present invention, since the stretching force F _p by the front wheel side of the air spring is smaller than the rear wheel side reduces the pressure supplied by that amount energy Can be made more efficient.

  According to the axle box support device of the present invention, the internal pressure supplied to the air spring is limited to a certain amount or less, so that the connecting portion does not expand even when a reverse steering command is input. . Therefore, even in the case of reverse steering, it is possible to suppress an increase in lateral pressure and realize a stable curve passing performance.

It is a side view of the railcar bogie provided with the axle box support device concerning an embodiment. It is a sectional side view of the axle box support device concerning an 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 sectional side view explaining operation | movement of an axle box support apparatus. It is a flowchart of operation | movement of an air spring control apparatus. (A) the internal pressure supplied to the air spring, (b) the extension of the connecting means, and (c) the lateral pressure when steering the outer gauge side front wheel and the inner gauge side front wheel. (A) the internal pressure supplied to the air spring, (b) the extension of the connecting means, and (c) the lateral pressure when steering the outer gauge side front wheel and the outer gauge side rear wheel.

DESCRIPTION OF EMBODIMENTS Hereinafter, embodiments 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 each end of the axle 32 of the wheel axle 30 to support the axle 30 so as to be rotatable, and the bearing supports the axle 32 so as to be rotatable about its axis. A shaft box body that accommodates the bearing, a lubrication device, and the like are provided.

  The axle box support device 50 is an apparatus for positioning and elastically supporting the axle box 40 with respect to the carriage frame 10. 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.

  And the connection means 60 is provided along the front-back direction between the trolley frame 10 and the axle box 40, and both ends can be rocked by pin joints with respect to the trolley frame 10 and the axle box 40, respectively. It is connected. 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 FIG. 2 in detail, the connecting means 60 is connected to the axle box side member 70 connected to the axle box 40 side, and is connected to the carriage frame 10 side to extend and contract the connecting means 60 relative to the axle box side member 70. A carriage side member 80, a cylindrical rubber bush 90, a return spring 100, and an air spring 110 that are relatively moved in the direction of movement (ie, the front-rear direction) are provided.

  The axle box side member 70 includes an axis portion 71, a flange 72, a bush holding portion 73, an axle box side bush 74, a stopper 75, and a nut portion 76.

  The shaft portion 71 is a cylindrical member extending along the longitudinal direction of the connecting means 60, and the axis O of the shaft portion 71 is provided at the end of the shaft box 40 side (left side in FIG. 2). A disk-shaped flange 72 is provided as a center and projects in the shape of a bowl outward in the radial direction.

  A bush holding portion 73 is formed on the surface of the flange 72 facing the axle box 40 so as to protrude from the surface, and the side surface of the bush holding portion 73 is in a direction perpendicular to the axis O on the raceway surface. That is, a through hole 73 a is formed in a direction parallel to the extending direction of the axle 32.

  A shaft box-side bush 74 that elastically supports the shaft box 40 with respect to the bush holding portion 73 is press-fitted into the through hole 73a. The axle box-side bush 74 is composed of an outer cylinder that is substantially cylindrical and press-fitted into the through hole 73a, and an elastic body (rubber or the like) that is disposed on the inner diameter side of the outer cylinder and forms an annular shape. Yes. Then, by inserting a pin supported by the connection portion 41 of the axle box 40 on the inner diameter side of the elastic body, the axle box side bush 74 is connected to the axle box 40 so as to be rotatable around the pin.

  The stopper 75 is fixed to an end portion of the shaft portion 71 on the cart frame 10 side (right side in FIG. 2), and has a disk shape projecting in a flange shape on the outer diameter side from the outer peripheral surface of the shaft portion 71. The stopper 75 restricts the stroke in which the shaft portion 71 moves relative to the outer cylinder 81 of the carriage side member 80 described later. This stroke is appropriately set according to the curvature of the curve of the route on which the vehicle travels and the geometric arrangement of the connecting means 60.

  The nut portion 76 is a member fixed to the surface portion of the flange 72 on the cart frame 10 side, and a distal end portion of a holding bolt 101 of a return spring 100 described later is inserted and screwed together.

  The cart side member 80 includes an outer cylinder 81, a flange 82, a bush holding portion 83, a cart frame side bush 84, a return spring seat 85, and an air supply hole 86.

  The outer cylinder 81 is substantially concentric with the shaft portion 71 described above, that is, has a cylindrical shape with the axis O as the center, and has an inner diameter larger than the shaft portion 71 and the shaft portion 71 is inserted on the inner diameter side. Is done. The outer cylinder 81 is movable relative to the shaft portion 71 along the axial direction O, that is, in the front-rear direction. Further, a flange 82 is formed at the end of the outer cylinder 81 on the cart frame 10 side so as to project from the outer peripheral surface to the outer diameter side in a collar shape.

  A bush holding portion 83 is formed on the surface of the flange 82 facing the carriage frame 10 so as to protrude from the surface, and the side surface of the bush holding portion 83 is in a direction perpendicular to the axis O on the raceway surface. That is, a through hole 83 a is formed in a direction parallel to the extending direction of the axle 32.

  And the bogie frame side bush 84 which elastically supports the bogie frame 10 with respect to the bush holding | maintenance part 83 is press-fit in this through-hole 83a. The carriage frame side bush 84 is formed of a substantially cylindrical outer cylinder that is press-fitted into the through-hole 83a, and an annular elastic body (rubber or the like) that is disposed on the inner diameter side of the outer cylinder. . Then, by inserting a pin supported by the connection portion 41 of the axle box 40 on the inner diameter side of the elastic body, the carriage frame side bush 84 is connected to the carriage frame 10 so as to be rotatable around the pin.

  In the present embodiment, the length direction of the connecting means 60 indicates the direction of a straight line connecting the centers of the axle box side bush 74 and the carriage frame side bush 84.

  The return spring seat 85 is a surface portion that comes into contact with the end portion of the return spring 100 on the axle box 40 side and holds the return spring 100, and is on the outer diameter side from the outer peripheral surface at the end portion of the outer cylinder 81 on the axle box 40 side. It is formed to protrude into. The return spring seat 85 is formed with an opening into which the holding bolt 101 of the return spring 100 is inserted.

  The air supply hole 86 is formed so as to communicate from the surface of the flange 82 facing the carriage frame 10 to the air chamber of the air spring 110 through the flange 82. A pipe for supplying internal pressure is connected.

The cylindrical rubber bushing 90 is arranged so as to fill a space between the outer peripheral surface of the shaft portion 71 of the axle box side member 70 and the inner peripheral surface of the outer cylinder 81 of the carriage side member 80. On the other hand, the shaft portion 71 is elastically supported.
The cylindrical rubber bush 90 includes an outer cylinder and an inner cylinder formed in a cylindrical shape, and the inner cylinder is inserted on the inner diameter side of the outer cylinder. The space between the inner peripheral surface of the outer cylinder and the outer peripheral surface of the inner cylinder is filled with, for example, a rubber-based elastic material, and is joined to the outer cylinder and the inner cylinder by vulcanization adhesion. The outer cylinder of the cylindrical rubber bush 90 is press-fitted into the inner diameter side of the outer cylinder 81 of the carriage side member 80, and the shaft portion 71 of the axle box side member 70 is inserted into the inner cylinder of the cylindrical rubber bush 90. . In the present embodiment, two such cylindrical rubber bushings 90 are provided in series in the axis O direction.
In this way, the cylindrical rubber bushing 90 mainly has the rubber part elastically deformed so that the shaft part 71 of the axle box side member 70 is in the axis O direction, that is, the front-rear direction with respect to the outer cylinder 81 of the carriage side member 80. It can be moved.

  The return spring 100 is a metal coil spring that urges the carriage-side member 80 in a direction in which the length of the connecting member is shortened with respect to the axle box-side member 70. And is arranged adjacent to the outer peripheral surface of the outer cylinder 81. The return spring 100 pre-compresses the connecting means 60 in the length direction thereof, so that the connecting means 60 maintains the basic length until the external force in the pulling direction reaches a certain level. It has become. A holding bolt 101 is disposed on the inner peripheral side of the return spring 100 so as to penetrate the return spring 100 in the axial direction.

The holding bolt 101 is inserted and screwed into the nut portion 76 of the axle box side member 70 from the cart frame 10 side. At this time, the intermediate portion of the holding bolt 101 is inserted into the return spring seat 85 of the carriage side member 80 and is movable along the axial direction with respect to the return spring seat 85.
In this way, the return spring 100 has the holding bolt 101 inserted on the inner diameter side, one end abuts the return spring seat 85 and the other end is locked to the head of the holding bolt 101. In a compressed state.

  The air spring 110 is a member that urges the cart side member 80 against the axle box side member 70 in a direction in which the length of the connecting means 60 is extended, and includes the bellows 111 and the pair of bellows holding members 112 and 113. I have.

  The bellows 111 is a cylindrical curtain body formed of an elastic body such as rubber, and an air chamber of an air spring 110 is formed therein. Inside the bellows 111, the above-described shaft portion 71, outer cylinder 81, return spring 100, and the like are arranged.

  The bellows holding members 112 and 113 fix the end portions of the bellows 111 on the axle box 40 side and the cart frame 10 side to the flanges 72 and 82, respectively. The bellows holding members 112 and 113 are formed by forming concave and convex portions that engage with the bead portions formed at the end portions of the bellows 111 on the inner edge of the annular plate. It is concluded.

  Further, the following air spring control device (not shown) is mounted on the air spring 110 of the axle box support device 50.

  The air spring control device extends the air spring 110 by supplying an internal pressure to the air spring 110 when the vehicle runs on a curve. As a result, the axle box side member 70 and the carriage side member 80 are separated from each other and the spring constant of the air spring 110 is increased.

When the vehicle is traveling straight, the air spring control device does not supply the internal pressure to the air spring 110. Therefore, the air spring 110 does not expand, and the spring constant of the air spring 110 is extremely low, and hardly acts as a spring element.
As a result, when the external force in the pulling direction does not substantially act on the connecting means 60 or when a relatively small tensile load that is input by the wheel snake behavior or the like during linear running acts, the shaft of the outer cylinder 81 The end on the box 40 side abuts on the flange 72, and the length of the connecting means 60 is maintained at the basic length which is the most compressed state. In other words, the value obtained by subtracting the urging force in the extension direction by the air spring 110 from the urging force in the compression direction by the return spring 100 is always larger than the maximum tensile force acting during linear running.
Therefore, during straight running, the rigidity of the connecting means 60 with respect to the tensile load (supporting rigidity in the front-rear direction of the wheel shaft 30) can be increased to prevent meandering of the wheel shaft 30 and to ensure running stability during straight running. It becomes possible.

On the other hand, when the vehicle is running on a curve, the air spring control device supplies the internal pressure to the air spring 110 on the outer gauge side. As a result, the air spring 110 is extended, and the spring constant of the air spring 110 is larger than the spring constant of the return spring 100. Normally, the internal pressure is not supplied to the air spring 110 on the inner gauge side during curve traveling, and the length of the connecting means 60 on the inner gauge side is maintained at the basic length.
Such supply of the internal pressure can be easily performed, for example, by providing a proportional control valve in the middle of a pipeline that supplies compressed air from the air reservoir of the vehicle to the air spring 110.
The vehicle can be detected on a curved line, for example, based on the output of a yaw rate sensor or a lateral G sensor provided on the vehicle body. At this time, the curvature of the curve may be obtained based on these outputs and the traveling speed of the vehicle, and the increase amount of the internal pressure of the air spring 110 may be increased as the curvature decreases. Alternatively, curve data of a route on which the vehicle travels may be stored in advance, and curve travel may be detected by comparing the travel position of the vehicle with the curve data.

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 cornering, the four front wheels 31a of the inner outside rail side of the wheel 31, the external force F _out of toward the vehicle forward traveling _direction, i.e., the external force F _out in the direction to separate the front wheel 31a from the carriage member 80 Is given from the rail.
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 direction to approach the front wheels 31b to carriage member 80 is provided from the rail.

の関係が成立した際、即ち、戻しバネ１００による圧縮力よりもレールから前輪３１ａに与えられる外力Ｆｏｕｔと空気バネ１１０による伸張力Ｆｐとの和が大きくなった際に、軸箱側部材７０と台車側部材８０とが離間して連結手段６０の長さが伸びることになる。 In light of this, that describes the relationship between the forces acting on the connecting means 60 at the time of cornering.
The front wheel 31a on the outer track side will be described with reference to FIG. 4A. The external force Fout applied to the front wheel 31a acts on the axle box side member 70 as a tensile load having the same magnitude.
In addition, a compression force Fs that causes the axle box side member 70 and the carriage side member 80 to approach each other by the return spring 100 acts, and further, an extension force Fp that causes the axle box side member 70 and the carriage side member 80 to be separated by the air spring 110. Works. When traveling on a curve, the internal pressure is supplied to the air spring 110 by the steering command of the air spring control device, and the extension force Fp by the air spring gradually increases. And

That is, when the sum of the external force Fout applied from the rail to the front wheel 31a and the extension force Fp by the air spring 110 becomes larger than the compression force by the return spring 100, the axle box side member 70 and The length of the connecting means 60 is extended by separating from the cart side member 80.

の関係が成立する。したがって、軸箱側部材７０と台車側部材８０とが離間することはなく連結手段６０の長さは基本長に維持される。 Also, when described with reference to FIG. 4 (b) for the front wheels 31b of the inner rail side, the external force F _in a given front wheel 31b acts as a similarly sized compression load with respect to the axle box member 70. Also, the return compressive force F _s to approach the axle box member 70 and the carriage member 80 is acted upon by a spring 100, further, stretching force to separate the axle box member 70 and the carriage-side member 80 by the air springs 110 F _p is applied. In addition, since the steering command from the air spring control device is not input on the inner rail side, the internal pressure is not supplied. Therefore, the extension force F _p by the air spring 110 is small, and always,

The relationship is established. Therefore, the axle box side member 70 and the carriage side member 80 are not separated from each other, and the length of the connecting means 60 is maintained at the basic length.

In this way, in the axle box support device 50 on the front wheels 31a, 31b side, only the connecting means 60 on the outer rail side extends. Also in the rear wheels 31c and 31d, the internal pressure is supplied to the air spring 110 on the outer wheel side by the steering command of the air spring control device during curve traveling, and only the connecting means 60 on the outer track side is expanded. As a result, the turning direction of each wheel 31 is matched with the tangential direction of the curve, and the lateral pressure is reduced.
Further, when the air spring 110 expands and the spring constant of the air spring 110 increases, the rigidity of the connecting means 60 with respect to the tensile load decreases. As a result, the connecting means 60 can be easily extended, so that the wheel shaft 30 can be steered more smoothly and the curve passing performance can be further improved.

の関係が成立した場合には、内軌側にも関わらず連結手段６０が伸張することになるためアタックアングルの増大とともに横圧が極端に増加してしまう。 Here, when a reverse steering command is input to the front wheels 31a and 31b due to some trouble to the air spring 110, that is, when internal pressure is supplied to the air spring 110 on the inner gauge side instead of the outer gauge side, or on the outer gauge side The case where the internal pressure is supplied to the air springs 110 on both the inner and the inner rail sides will be considered.
In this case, as shown in FIG. 4B, a compressive load caused by the external force F _in applied to the wheel from the rail, a compressive force F _s by the return spring 100, and an extension force F _p by the air spring 110 act. . When the stretching force _{F p} by the air spring 110 is greater than the sum of the compressive force _{F s} of the spring 100 back to the external force _{F in} receiving from the rail, i.e.,

When the above relationship is established, the connecting means 60 is extended regardless of the inner track side, so that the lateral pressure increases extremely as the attack angle increases.

の関係を満たすように、前輪３１ａ、３１ｂ側の各空気バネ１１０内圧の供給量が制限されている。即ち、本実施形態においては、前輪３１ａ、３１ｂ側の空気バネ１１０による伸張力Ｆ_ｐの最大値が、内軌側の前輪３１がレールより受ける外力Ｆ_ｉｎと戻しバネ１００による圧縮力Ｆ_ｓとの和以下となるように制限されているのである。したがって、内軌側の連結手段６０が伸張することがないため、逆操舵の場合における極端な横圧の増加を防止することができる。これにより、安定した曲線通過性能を実現することが可能となる。 In this way, in the axle box support device 50 of the present embodiment, the value of the extension force F _p generated by the internal pressure supplied to the air spring 110 is such that the inner rail side connecting means 60 does not extend.

The supply amount of the internal pressure of each air spring 110 on the front wheels 31a and 31b side is limited so as to satisfy the above relationship. That is, in the present embodiment, the maximum value of the extension force F _p by the air spring 110 on the front wheels 31 a and 31 b side is the external force F _in that the inner wheel side front wheel 31 receives from the rail and the compression force F _s by the return spring 100. It is limited to be less than the sum of. Therefore, the connecting means 60 on the inner rail side does not expand, and therefore an extreme increase in lateral pressure in the case of reverse steering can be prevented. This makes it possible to achieve stable curve passing performance.

Incidentally, the external force F _in the curve inside wheels receive the curve radius, speed, angle of attack, lateral force, wheel load, lateral vibration of the wheels, wheel tread shape, rail cross section, each parameter of the material of the wheel and the rail Dependent. Therefore, the maximum value of the stretch force F _p by the air spring 110 is defined by the above parameters. It is also possible to previously held the curve data of the rail vehicle from the information travels determines the maximum value of the stretch force F _p by comparing running position and curve data of the vehicle.

The operation procedure of the air spring control device that performs steering as described above will be described with reference to the flowchart shown in FIG.
First, the air spring control device detects whether or not the vehicle is traveling in a curved line, that is, whether or not the track on which the vehicle travels is a curved line or a straight line (step S1). This detection method is as described above.

  When it is determined that the vehicle is traveling in a straight line, the air spring control device does not supply internal pressure to the air spring 110, and the connecting means 60 is maintained at the reference length without extending. Thereby, the rigidity of the connection means 60 is ensured. Then, it is determined whether or not the control state is good, that is, whether or not the internal pressure is appropriately in a non-supply state. (Step S4).

が満たされる伸張力Ｆ_ｐを定め、この伸張力Ｆ_ｐを発生することが可能な内圧を最大内圧として制限する（ステップＳ２）。 On the other hand, when it is determined that the curve direction, the maximum value of the stretch force F _p by the air spring 110, namely,

It defines the stretch force F _p which is satisfied, to limit the maximum pressure the pressure that can be generated this stretching force F _p (step S2).

  Next, the internal pressure equal to or lower than the maximum internal pressure is supplied to the air spring 110 corresponding to the front wheel 31a on the outer track side when passing through the curve to steer the wheel shaft 30 (step S3).

Subsequently, it is determined whether or not the control state is good, that is, whether or not the vehicle is in a non-steering state in the case of straight traveling and is in an appropriate steering state in the case of curved traveling. (Step S4).
Then, steps S1 to S4 are repeated until the control state is stabilized, thereby preventing the occurrence of lateral pressure during curve traveling and preventing an extreme increase in lateral pressure during reverse steering.

Note that in the axle box support device 50 of this embodiment, the extensional force of the air spring 110 _{F p} is the rear wheels 31c, the front wheels compared to 31d side 31a, so as to reduce the 31b side, the air spring air spring control means It is preferable that the internal pressure is supplied to 110.

As described above, when the vehicle is traveling in a curved line, the external force F _{out is applied} from the rail to the front wheel 31a on the outer track side. Thus, the front wheels 31a of the curve outside can be easily stretched by receiving support stretching force F _p is small with the F _out by the air spring 110, it is possible to suppress the lateral pressure.
Therefore, the axle box support device 50 of the present embodiment, the front wheels 31a, by reducing as compared with the rear wheel 31 side stretching force F _p by the air spring 110 31b side, thereby reducing the internal pressure supplied by that amount Energy efficiency can be improved.

The embodiment of the axle box support device 50 of the present invention has been described above, but the present invention is not limited to this, and can be appropriately changed without departing from the technical idea of the present invention.
For example, in the embodiment, it has been described that an increase in lateral pressure can be prevented even in the case of reverse steering, but the present invention is not limited to this. It is good also as a structure by which an internal pressure is simultaneously supplied to the air spring 110 of a side and an outer track side. As a result, on the outer track side, the steering is easily performed by receiving the support of the external force Fout received from the rail, while on the inner track side, the extension is suppressed by the external force Fin received from the rail, and the connecting means 60. The compressed state is maintained. This also makes it possible to improve the curve running performance of the vehicle without excessively increasing the lateral pressure. Even in this case, limiting the maximum value of the extension force Fp by the air spring 110 in the same manner as described above is an essential requirement for preventing an extreme increase in lateral pressure.

A test was conducted to measure the elongation of the connecting means 60 and the lateral pressure applied to the wheels 31 during steering and reverse steering.
Specifically, a carriage 1 having two wheel shafts 30 as shown in FIG. 3 and having a wheel box support device 50 mounted on each of four wheels 31 (front wheels 31a, 31b, rear wheels 31c, 31d) is R400. In the case of traveling at a speed of 65 km / h, the elongation and lateral pressure of the connecting means 60 when steering and reverse steering commands were input were measured.

FIG. 6 shows the results when steering the outer track side front wheel 31a and the inner track side front wheel 31b. 6, (a) shows the internal pressure supplied to the air spring at the time of steering, (b) shows the extension of the connecting means, (c) shows the lateral pressure, and in each graph, the horizontal axis shows the elapsed time. Yes.
First, when only the outer gauge side front wheel 31a is steered as shown in the mountain on the left side of FIG. 6A, as shown in FIG. It becomes the maximum at the stage of 500 kPa. Further, as shown in (c), the lateral pressure is reduced as the supply internal pressure is increased and the connecting means 60 is extended, but the lateral pressure is minimized when the internal pressure is 300 kPa.
Therefore, it was found that when only the outer-gauge front wheel 31a is steered, the lateral pressure can be effectively reduced by the operation of supplying a relatively small internal pressure to the air spring 110.

  Next, when only the inner track side front wheel 31b is steered as shown in the mountain near the center of FIG. 6A, that is, in the case of reverse steering, the supply internal pressure is more than a certain value as shown in FIG. In this embodiment, the connecting means 60 on the inner track side does not extend until it exceeds 500 kPa. Further, as shown in (c), the lateral pressure does not increase until the internal pressure exceeds 500 kPa and the inner rail side connecting means 60 is elongated. Therefore, in the case of the present embodiment, if the maximum internal pressure supplied to the air spring 110 is limited to 500 kPa or less, it is possible to prevent the lateral pressure from increasing extremely even in the case of reverse steering. In addition, even if the internal pressure supplied to the air spring is 300 kPa as described above, the lateral pressure can be sufficiently reduced during proper steering, so from the viewpoint of energy efficiency, It is appropriate to set the maximum internal pressure to 300 kPa.

  Then, as shown in FIG. 6 (a), the outer gauge side front wheel 31a and the inner gauge side front wheel 31b are simultaneously steered, as shown in FIG. 6 (a). As for the inner rail, the elongation increases as the internal pressure increases, and the inner rail side connecting means 60 does not extend unless the internal pressure exceeds 500 kPa. Further, even when the outer rail side and the inner rail side are steered at the same time, the lateral pressure is reduced, and a sufficient lateral pressure reducing action is obtained until the inner rail side connecting means 60 is stretched. Can do. Therefore, by limiting the maximum internal pressure supplied to the air spring 110 to 500 kPa or less, it is possible to appropriately reduce the lateral pressure even in the case of simultaneous steering on the outer gauge side and the inner gauge side. I understood. Also in this case, since the lateral pressure can be sufficiently reduced when the internal pressure supplied to the air spring is 300 kPa, it is appropriate to set the maximum internal pressure to 300 kPa from the viewpoint of energy efficiency.

  FIG. 7 shows the results when the outer track side front wheel 31a and the outer track side rear wheel 31c are steered simultaneously. Also in FIG. 7, as in FIG. 6, (a) shows the internal pressure supplied to the air spring during steering, (b) shows the extension of the connecting means, and (c) shows the lateral pressure. Indicates the elapsed time.

During cornering, the external force _{F out} is given from the rail to the front wheels 31a of the curve outside. Therefore, it can be considered that the front wheel 31a side on the outer track side can sufficiently extend with the support of the external force even if the internal pressure supplied to the air spring 110 is smaller than that on the rear wheel 31c side. FIG. 7 shows the results of a test conducted based on such knowledge. Specifically, as shown in FIG. 7A, the outer-gauge front wheel 31a and the outer-gauge side rear wheel 31c are steered simultaneously. At this time, the steering is performed so that the internal pressure supplied to the air spring 110 of the outer gauge side front wheel 31a is smaller than the internal pressure supplied to the air spring 110 of the outer gauge side rear wheel 31c.
When this result is seen, as shown in FIG.7 (b), both the connection means 60 of the outer gauge side front wheel 31a and the connection means 60 of the outer gauge side front wheel 31b are extended with the increase in internal pressure, and the outer gauge in this case The lateral pressure of the side front wheel 31a and the inner track side front wheel 31b is greatly reduced as shown in FIG.
Therefore, it is possible to obtain a very high lateral pressure reduction effect by simultaneously steering the front wheel 31a and the rear wheel 31c on the outer track side, and this effect sets the internal pressure of the air spring 110 of the front wheel 31a on the outer track side low. It was confirmed that it can be obtained even in the case of. Thus, it was found that the supply energy of the internal pressure can be reduced.

1 dolly
10 Bogie frame 20 Bogie air spring
30 wheel shaft 31 wheel 31a front wheel 31b front wheel 31c rear wheel 31d rear wheel 32 axle 40 axle box 50 axle box support device
60 connecting means
70 Axle box side member 80 Dolly side member 86 Air supply hole
100 Return spring
110 Air spring

Claims (1)

An axle box support device that supports axle boxes provided at both ends of the front and rear wheel axles of a railway vehicle carriage with respect to the carriage frame of the carriage by connecting means extending along the traveling direction of the vehicle. And
The connecting means includes
The axle box side member attached to the axle box,
A carriage side member attached to the carriage frame and connected to the axle box side member so as to be relatively displaceable in a traveling direction of the vehicle;
A return spring that is provided between the axle box side member and the cart side member, and generates a compression force Fs that causes the axle box side member and the cart side member to approach each other;
An air spring that is provided between the axle box side member and the carriage side member and generates an extension force Fp that separates the axle box side member and the carriage side member in accordance with the supplied internal pressure;
An air spring control means for supplying a predetermined internal pressure to at least the air spring on the outer track side to increase the extension force Fp of the air spring when the vehicle is running on a curve;
For the external force Fin along the vehicle traveling direction that the front wheel traveling on the inner rail side receives from the rail, the air spring control means,

Relationship as is true, limits the pressure supplied to each of the air springs of the outer rail side and the curve inside the front wheel,
The axle box support device , wherein the internal pressure is supplied to the air spring so that the extension force Fp by the air spring is smaller on the front wheel side than on the rear wheel side .

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