KR101198916B1 - Apparatus for testing wheel of railway vehicle and rail with elastic member for removing noise of thrust load or radial load - Google Patents

Abstract

The present invention discloses an apparatus for testing wheels and rails of a railway vehicle having an elastic member for improving high frequency component removal efficiency of force generated when side loads and load loads are applied, and for easily adjusting elastic modulus. The disclosed wheel and rail test apparatus includes a load load that imparts a radial load to a wheel specimen in a radial direction of the wheel specimen, and is disposed on one side of the wheel shaft to apply a side load to the wheel specimen. And a wheel specimen driving unit configured to apply side loads and wheel shafts to which the wheel specimens and the wheel shafts are attached and to rotate the wheel shafts to rotate the wheel specimens, thereby applying side loads and load loads to the wheel specimens. A rail specimen driving unit having a rail shaft coupled to the rail shaft and a rail driving unit rotating the rail shaft, the rail specimen driving unit being separately disposed with the wheel specimen driving unit parallel to the wheel shaft; and a load spring having a plurality of coil springs. And an elastic member installed in an axial direction where a load is applied in at least one of the side loads to remove high frequency components of the applied load. And that is characterized.

Description

APPARATUS FOR TESTING WHEEL OF RAILWAY VEHICLE AND RAIL WITH ELASTIC MEMBER FOR REMOVING NOISE OF THRUST LOAD OR RADIAL LOAD}

The present invention relates to an apparatus for testing wheels and rails of a railway vehicle, and more particularly, an elastic member for improving high frequency component removal efficiency of force generated when side loads and load loads are applied, and for easily adjusting elastic modulus. It relates to a wheel and rail test apparatus of a railway vehicle having a.

Since a railroad vehicle performs linear, curved, meandering motions on rails, a large load acts at various angles between steel wheels and wheels. Therefore, when the wheels and rails of a railroad car are worn out by the frictional force due to the driving motion of the railroad car and a large load, the wheels and rails of the railroad car generate unstable contact between the wheels and the rails. Such unstable contact may prevent the railway vehicle from stably supporting during various driving motions of the railway vehicle, or may cause railway accidents due to wheel or rail breakage.

Accordingly, through the fatigue or wear test of wheels and rails of railway vehicles, various phenomena occurring due to various contact of wheels and rails should be identified and reflected in the design of wheels and rails.

An example of a device for performing a test according to various contact conditions or loads while driving such wheels and rails is 'rail and wheel fatigue test device' of JP-A-63-198848 (JP1998-198848) (Prior Art 1). ) And "Electric Fatigue Tester" (Prior Art 1) of JP-A-58-53736 (JP 1983-53736).

The prior art 1 is a test wheel device having a test wheel (rail: rail) fixed to the side wall of the side loading mechanism having a hydraulic servo cylinder to be suspended by the guide rail and the block; and, the test wheel device Wheel contacting the test wheel in the direction orthogonal to the wheel, and the attack angle granting mechanism for giving the attack angle so that the wheel is in torsional contact with the test wheel, and the wheel by the reducer through the attack angle granting mechanism and the connecting pipe. And a brake device unit including a wheel centering tool for applying a load to the wheel, and a contact angle exciter which is equipped with a wheel, an attack angle applying machine, and a wheel loading device, which rotates around a point of attachment. The wheel and rail side loads (thrust loads), contact angles, loads, and torsion angles (attack angles) can be adjusted to test the wheel and rail fatigue.

In the prior art 2, the rail test piece and the wheel test piece are respectively coupled to the test piece mounting shafts whose shafts are separated from each other by the spindle drive motor and the continuous gear mechanism, respectively, by the load means, the vertical load arm and the thrust box. A vertical load is applied to the wheel from the vertical direction to the downward direction, and a lateral pressure (thrust load) is applied to the wheel by rotating the screw bolt using the horizontal pressure adjusting handle, and the cam protrusion is used. And a lateral pressure load device for applying the rotational motion of the lateral load motor to the left and right swing (meaning motion) of the wheel test piece. The prior art 2 of the above configuration applies a radial load in the vertical downward direction and applies a thrust load by a lateral pressure load device so as to perform a contact test between the wheel and the rail of the train.

However, in the related art 1, since the side load (thrust load) is applied to the wheel side after the side load (thrust load) is applied to the rail side, the side load (thrust load) in the actual situation is inclined or meandering of the vehicle. As the driving is reversed from being applied from the wheel (wheel) side to the rail side, there is a problem in that the driving motion of the actual railway vehicle cannot be accurately reproduced.

Next, in the case of the prior art 2, since the radial load and the side load (thrust load) of the train are applied by the screw screw, it is difficult to accurately apply the force, and to apply the force automatically. There is a problem that a separate device for the operation of the handle is required.

In addition, in the case of the prior art, the side load (thrust load) is configured such that the force is transmitted by a coupler, a ball spline, or the like (prior art 1), or a force is cut through a screw bolt, a wet bearing, etc. Technology 2) There is a problem that the response characteristics of the load transmitted to the wheel is degraded because there is no configuration for removing the high frequency components of the load.

That is, in the case of the conventional techniques, the difference between the side load (thrust load) applied by the hydraulic servo cylinder and the side load (thrust load) actually applied to the rail, or the load to be applied to the wheel and the wheel Differences can arise between the actual loads that are present, which leads to problems that can reduce the accuracy of the test.

The present invention is to solve the problems of the prior art, the wheel and rail testing apparatus of a railway vehicle having an elastic member to remove the high frequency components that are noise components of the force generated when the side load and load load is applied To provide that purpose.

It is another object of the present invention to provide a wheel and rail testing apparatus for a railway vehicle having an elastic member to easily adjust the elastic modulus or stiffness to remove the high frequency component of the force.

In addition, the present invention performs an accurate wheel and rail test by realizing the load action acting on the wheels and rail of the actual railway vehicle by easily applying a thrust load and a radial load to the wheel Another object is to provide a wheel and rail testing apparatus for railway vehicles that can be used.

Wheel and rail test apparatus of the railroad vehicle having an elastic member for removing high-frequency components of the side load and the load load of the present invention for achieving the above object, the radial load on the wheel specimen in the radial direction of the wheel specimen A load load to impart a load), a side load to be disposed on one side of the wheel shaft to impart a thrust load to the wheel specimen, and the wheel specimen and the wheel shaft are mounted to rotate the wheel shaft. A wheel specimen driving unit configured to apply a side load and a load load to the wheel specimen by rotating the wheel driving unit; and a rail shaft to which the rail specimen is coupled and a rail driving unit to rotate the rail shaft to parallel the wheel shaft. A rail specimen driving part separated from the driving part; and a plurality of coil springs which can be adjusted in number, and at least one of the load load and the side load. And an elastic member for eliminating high frequency components of the applied load to be applied is provided on the axial direction; including and being configured.

The load may include: a swivel joint fixed to a mounting jig; an actuator having one end coupled to the swivel joint; and a load detection unit coupled to the other end of the actuator; and an actuator of the elastic member. One end is coupled to the opposite end of the end portion and the other end is a load rod (rod) coupled to the lower support of the wheel driving portion, wherein the elastic member is an area between any one of the actuator and the load detection unit and the load rod Can be configured.

The side load includes: a mounting jig; a swivel joint fixed to the mounting jig; an actuator coupled to the swivel joint; and a load detection unit coupled to the other end of the end to which the swivel joint of the actuator is coupled; And a side rod coupled to an opposite end of the end axially coupled to the load detection unit on one side in the axial direction, and the other end coupled to the wheel driving unit, wherein the elastic member includes the actuator and the load. It may be configured in an area between any one of the detector and the side rod.

The elastic member may include a first support plate having a plurality of first fixing tubes; a second support plate having a plurality of second fixing tubes; and a plurality of coil springs of which the number is adjusted. The first fixing tube and the second fixing tube are coupled to each other so that the first fixing tube and the second fixing tube is coupled to the outer periphery of the first fixing tube and the second fixing tube so as to be deformable in length and coupled to both ends of the coil spring. Each may be coupled to be elastically supported on the first support plate and the second support plate.

The wheel driving unit includes: at least one spindle rotatably supporting the wheel shaft; and a lower support to which the spindle is detachably installed and to which a load rod of the load is coupled; It may further comprise a support.

The wheel driving unit may further include a side driving plate on which a wheel shaft support for supporting the wheel shaft to which the wheel specimen is coupled is installed, and the side driving plate is moved in the side load direction according to the side load and is not moved in the other direction. At least one side rail supporting the driving plate, a load driving plate installed on the upper surface of the side rail, and the load driving plate is moved in the load direction in accordance with the load and is not moved in the other direction. At least one load guide rail for supporting the load driving plate; may further comprise a linear movement guide including a.

The rail specimen driving unit may further include a rail shaft support including a plurality of spindles rotatably supported by the rail shaft, and a vertical support attached to a bottom surface of the spindle such that the spindle is detachable. have.

The present invention having the above-described configuration improves the load response characteristics of the wheel specimen by removing the high frequency components of the load applied to the wheel specimen by the elastic members provided at the load loading and the side loading. Since the width of the load or side load to be applied to the wheel specimen is changed less, it provides the effect of obtaining more accurate test results such as fatigue or wear of the wheel and rail.

The present invention also provides that the load load, the side load and the wheel drive are fixedly installed on the wheel drive plate so that the side load and the radial load are converted in a straight line in which the load is applied. Is applied to the wheel specimen without Therefore, the load applied during the application of thrust load and radial is applied to the wheel specimen without any loss. Therefore, the load response characteristics of the wheel specimen are improved, making it easier to apply the load and the accuracy of the test results. It also provides a boosting effect.

The present invention also applies a load load and a side load to the wheel specimen, thereby reproducing the same environment in which the load load and the side load are applied to the rail by the wheel in the driving state of the actual railway vehicle. The ability to perform wheel and rail tests in close proximity to real-world driving conditions further enhances the accuracy of wheel and rail test results.

The invention also provides for the replacement, repair and mounting of wheel specimens, wheel axles and spindles by the wheel axle support comprising a lower support to which the load rod is coupled after the spindle and the spindle are detachably attached to the spindle. This facilitates the testing of wheels and rails.

1 is a perspective view of a wheel and rail tester having a thrust loader and a radial loader according to an embodiment of the present invention;
2 is a perspective view of the wheel specimen driving unit 100 of the configuration of FIG.
3 is a partial perspective view of the wheel driving unit 170 for showing the detailed configuration of the linear movement guide 190 of the configuration of FIG.
4 is a rear view of the rail specimen driving unit 300 viewed from the IV direction of FIG.
5 is an exploded perspective view of the load load spring 120.

Hereinafter, with reference to the accompanying drawings showing a preferred embodiment of the present invention will be described in more detail the present invention.

In the description of the embodiment of the present invention, the surface viewed in the direction of the IV arrow based on the direction of the IV arrow in FIG. The side viewed from the left side of the direction is called the left side.

In the description of the embodiments of the present invention, in order to clearly identify the configuration according to the configuration of the side loading or loading, the names are given so as to be identified by describing 'side' or 'load' in front of the name. Embodiments of the elastic member, the actuator, the mounting jig, the rod, the driving plate, the swivel joint, and the like are provided. The side load cell and the load load cell in the description of the embodiment of the present invention are embodiments of the load detection unit of the present invention.

1 is a wheel and rail test apparatus 1 (hereinafter, 'wheel and rail test') having a thrust loader 140 and a radial loader 110 according to an embodiment of the present invention. 2 is a perspective view of the wheel specimen driving unit 100 in the configuration of FIG. 1, and FIG. 3 shows a detailed configuration of the linear movement guide 190 in the configuration of FIG. Is a partial perspective view of the wheel driving unit 170 for.

As shown in FIG. 1, the wheel and rail test apparatus 1 according to the exemplary embodiment of the present invention has a wheel specimen 10 mounted thereon, and has a side load and a radial load on the wheel specimen 10. A rail specimen driving unit installed on a vertical wall surface facing the wheel specimen driving unit 170 on a wheel specimen driving unit 100 configured to apply the wheel jig and a fixed jig 310 fixed in parallel to the wheel axis of the wheel specimen driving unit 100 ( 300, and the hydraulic distribution unit (H), the wheel specimen driving unit 100, the rail specimen driving unit 300 and the base plate (500) for fixing the hydraulic distribution unit (H). .

The hydraulic distribution unit (H) is to perform the function of distributing the hydraulic pressure supplied to the load load 110 and the side load 140 of the wheel specimen driving unit 100 is composed of HSM (Hydraulic service manifold) Can be.

As shown in FIG. 2, the wheel specimen driving unit 100 includes a load loading unit 110, a side loading unit 140, and a wheel driving unit 170 integrally mounted on the wheel driving plate 210.

The load load 110 is a load mounting jig 111, a load swivel joint 113, a load actuator 115 and a load load cell 116 are sequentially coupled in the axial direction to apply a load load It is configured to be fixed on the wheel drive plate 210 including an overload load spring 120 and a load rod (117).

The load mounting jig 111 is fixed to the wheel driving plate 210 in the radial direction of the wheel specimen 10.

The load swivel joint 113 is rotatably fixed to a surface opposite to the center of the wheel specimen 10 of the load mounting jig 111.

The load actuator 115 is configured as a hydraulic servo actuator to generate a load load corresponding to the load to be applied to the wheel specimen.

The load load cell 116 is coupled between the load actuator 115 and the load load spring 120 is configured to detect and output the load load value applied from the load actuator 115 to the load rod (117) .

The load load spring 120 removes a high frequency component that is a noise component of the force by performing a damping function for the load applied from the load actuator 115. In addition, the load load spring 120 is configured to easily adjust the elastic modulus (stiffness) to facilitate the removal of high frequency components. The load load spring 120 is described in more detail below with reference to FIG. 5.

The load rod 117 has one end in a single shaft shape, and the other end is configured to have branches branched in a 'c' shape. The load rod 117 of the above configuration has a single shaft end portion coupled to the load load cell 116, and the branch end portion has a lower support 177b of the wheel shaft support 177 which will be described below. The load load generated from the load actuator 115 is coupled to the wheel specimen (10).

The side loading 140 is the side mounting jig 141 and the side swivel joint 143 and the side actuator 145 which are sequentially coupled along the axial direction to apply the side load in the axial direction of the wheel specimen 10 and A side load cell (thrust load cell) 146, the side load spring 150 and the side rod (rod) 148, including a fixed configuration on the wheel drive plate (210).

The side mounting jig 141 is fixed to the wheel driving plate 210 in the direction of the wheel shaft 173 of the wheel specimen 10.

One side end of the side swivel joint 143 is rotatably fixed to a surface opposite to the center of the wheel specimen 10 of the side mounting jig 141 and the other end is coupled to the side actuator 145.

The side actuator 145 is configured as a hydraulic servo actuator to generate a side load applied along the axial direction of the wheel shaft 173 to apply the side load to the side of the wheel specimen 10.

The side load cell 146 is coupled between the side actuator 145 and the side load spring 150 and is configured to detect and output a side load value applied to the wheel specimen 10 from the side actuator 145.

The side load spring 150 is configured such that one end is coupled to the side load cell 146 and the other end is coupled to the side rod 148.

The side rod (148) is coupled to one side of the side load spring 150 and the other end is coupled to the side of the side drive plate 192 of the linear movement guide 190 described below.

The wheel driver 170 includes a wheel driver 171, a wheel shaft support 177, a wheel shaft 173, a wheel specimen 10, and a wheel shaft support 177 so that the front and rear linear movements of the wheel driver 171 are performed. Is fixedly configured on the wheel drive plate 210.

The wheel driver 171 is composed of a servo motor that can control the rotational speed to the wheel driving plate 210 of the position opposite to the side loading 140 in the direction of the wheel shaft 173 of the wheel specimen 10 It is fixedly installed. The rotation axis of the wheel driver 171 is coupled to the wheel shaft 173 rotatably supported on the wheel shaft support 177 by a coupler C, such as a CV joint (Constant Velocity joint) to the wheel shaft 173 desired speed. Rotate to

The wheel shaft support 177 is configured at each of both ends of the wheel shaft 173. Each wheel axle support 177 has a load spindle 177a on which both ends of the wheel shaft 173 are rotatably supported, and an upper portion on the bottom of the load spindle 177a so that the load spindle 177a can be attached and detached. The surface is coupled and the bottom surface includes a lower support 177b fixedly mounted on the upper side of the side driving plate 192 of the linear movement guide 190 to be described below.

The wheel specimen 10 becomes a wheel of a railway vehicle.

As shown in FIG. 3, the linear movement guide 190 includes a side driving plate 192, a plurality of side guide rails 194, a load driving plate 196, and a plurality of load guide rails 198 from top to bottom. The load guide rails 198 are fixed to the wheel driving plate 210.

The lower support 177b of the wheel shaft support 177 is fixedly installed on the upper side of the side driving plate 192, and the side rod 148 is coupled to the side opposite to the side loading 140.

The side guide rails 194 are attached to the bottom surface of the side driving plate 192 so that the side driving plate 192 can be moved left and right through the guide block 191, the bottom surface of the load driving plate 196 It is fixed at the top.

The load driving plate 196 is coupled to the bottom surface by a plurality of load guide rails 198 so as to be movable in the front and rear directions through the guide block 191.

The load guide rails 198 have a bottom fixedly coupled to the wheel driving plate 210.

The linear movement guide 190 having the above configuration is moved on the side rail 194 of the side drive plate 192 when the side load is applied, but the load drive plate 196 is not moved on the load guide rail 198. Will not. In addition, when the load is applied, the load driving plate 196 is moved on the guide rail 198, but the side portion is not moved on the guide rail 194. That is, the linear movement guide is moved only in the direction of the application of force, thereby preventing the occurrence of free freedom of movement in the undesired direction when the force is applied.

4 is a rear view of the rail specimen driving unit 300 viewed from the IV direction of FIG. 1 in the configuration of FIG. 1.

1 and 4, the rail specimen driving unit 300 is fixed on the base plate 500 to form a vertical wall surface 310a facing in parallel to the wheel shaft 173 of the wheel specimen driving unit 100 It comprises a jig 310, a rail driving plate 410 provided on the vertical wall surface 310a and a rail driving unit 370 mounted to hang on the rear surface of the rail driving plate 410.

The rail driving unit 370 includes a rail shaft 373 on which the rail specimen 20 and the rail specimen 20 are axially coupled, and two rail shaft supports 377 on which both ends of the rail shaft 373 are rotatably supported. And a rail shaft 373 supported by the rail shaft support 377, a rail driver axially coupled with the rail shaft 373, and a rail shaft 373 of the rail driver 371. It is configured to include a braking portion (B) coupled to the shaft of the other end.

The rail driver (rail driver) is composed of a servo motor capable of controlling the rotation speed.

The rail shaft support 377 includes two rail spindles 377a for rotatably supporting both ends of the rail shaft 373, and a rear vertical wall surface 310a of the fixing jig 310 to detachably mount the rail spindles 377a. It is configured to include a vertical support (377b) fixed to). By the above configuration, the rail spins 377a can be separated from the vertical support 377b, thereby facilitating replacement, repair, etc. of the rail spins 377a, the rail shaft 373 and the rail specimen 20.

The rail specimen 20 is formed in a circular shape on the outer periphery of the rail of the railway.

5 is an exploded perspective view of the load load spring 120 and the load load spring 120 will be described in more detail with reference to FIG. 5 as follows.

As shown in FIG. 5, the load load spring 120 is coupled to the lower load cell shaft 116a attached to the load load cell 116, and a first fixing tube in which one end of the plurality of coil springs 125 is inserted and fixed, respectively ( Second support plate having a first support plate 121 having a 122, a plurality of coil springs 125, and the second fixing tube 127 is inserted and fixed to the other end of the plurality of coil springs 125, respectively And 126.

The second fixing tube 127 has an outer diameter smaller than the inner diameter of the first fixing tube 122 or vice versa so that the first fixing tube 122 and the second fixing tube 127 may vary in length in the longitudinal direction. To be combined. At this time, the coil spring 125 is coupled to the outer periphery of the first fixing tube 122 and the second fixing tube 127 connected to each other, and then both ends of the coil spring 125 are connected to the first supporting plate 121 and the second supporting plate 126. Each is coupled to be elastically supported.

By the combination as described above, the integrated load spring 120 is assembled.

The load load spring 120 and the side load spring 150 having the above-described configuration may be disposed between any one of the load actuator 115, the load load cell 116, and the load rod 117 or the side actuator 145. A load load applied from the load actuator 115 by performing a damping action by being placed on an axis through which a load load or side load, such as between the side load cell 146 and the side rod 148, is transmitted. Alternatively, the high frequency component of the side load applied from the side actuator 145 is removed.

In this case, the elastic modulus or rigidity of the load load spring 120 is easily adjusted by adjusting the number of the coil springs 125 when the modulus of elasticity or stiffness is necessary to improve the efficiency of the high frequency component removal of the load load or the side load. It can be adjusted.

Accordingly, the high frequency component of the force unnecessarily generated in the test at the time of applying the load load or the side load is effectively removed, so that the desired force (load) is applied to the wheel specimen 10 so as to accurately test the fatigue or wear of the wheel and rail. And the test results are also closer to the fatigue and wear of the actual wheels and rails.

The load load spring 120 and the side load spring 150 are embodiments of the elastic member of the present invention. In the description of the embodiment of the present invention, the side load spring 150 may also be configured to have the same configuration as the load load spring 120. Therefore, when the side load spring 150 has the same structure as the load load spring 120, the adjustment of the rigidity or elastic modulus is adjusted by adjusting the number of coil springs.

The wheel and rail test apparatus 1 of the present invention having the above-described configuration rotates the wheel specimen 10 using the wheel driver 171 after contacting the wheel specimen 10 and the rail specimen 20, and the rails. The wheel and rail test can be performed while rotating the rail specimen 20 using the driver 171.

That is, when the wear due to the radial load between the wheel and the rail is to be tested, the load to be tested is applied to the wheel specimen 10 by using the load actuator 145 and the load load cell 116. In addition, when applying a side load (thrust load) by applying the side load to the wheel specimen 10 by using the side actuator 145 and the side load cell 146 of the side loading 140 to the wheel and rail Allow fatigue or wear tests to be performed. During this test, the load and side loads may be applied to the wheel specimen at the same time.

That is, in the present invention, the load load 110, the side load 140, and the wheel driver 170 are all fixedly installed on the wheel drive plate 210, so that the side load and thrust load are radial. Since the load is applied to the wheel specimen 10 on the straight line formed by the shafts, the load applied when the thrust load and the radial load are applied to the wheel specimen 10 without causing a loss of the wheel specimen. The load application and response characteristics of (10) are improved to facilitate the application of load and to improve the accuracy of the test results.

In addition, the present invention the wheel by removing the high frequency component of the load to which the load load spring 120 or the side load spring 150 as the elastic member provided in the load load 110 and the side load 140 The load response characteristic in the specimen 10 is improved. In other words, since the width of the load or side load to be applied to the wheel specimen is changed less, the more accurate test results such as fatigue or wear of the wheel and rail can be obtained.

In addition, since the present invention applies the load load and the side load to the wheel specimen 10, it is possible to reproduce the same environment as the load load and the side load is applied to the rail by the wheel in the running state of the actual railway vehicle. This makes it possible to perform wheel and rail tests in close proximity to the actual conditions of rolling stock, further improving the accuracy of the wheel and rail test results.

In addition, the present invention is that the linear movement guide 190 is configured such that the movement in the other direction is fixed when moving in one direction, so that the degree of freedom does not occur when the side load or the load is applied, so as to test the fatigue or wear of the wheel and the rail. Further improves accuracy.

In the present invention, a contact angle between the wheel specimen 10 and the rail specimen 20 is given by rotating the wheel driving plate 210. An attack angle causing the torsional contact between the wheel specimen 10 and the rail specimen 20 is given by rotating the rail driving plate 410 up and down about the center of the rail specimen 20.

1: wheel and rail tester, 10: wheel specimen, 20: rail specimen, 100: wheel specimen driver
110: loading, 113; Load mounting jig, 113: load swivel joint, 115: load actuator, 116: load load cell, 117: load rod
120: load load spring, 121: first support plate, 122: first fixing tube, 125; Coil spring, 126: second support plate, 127: first fixing tube
140: sideloading, 141; Side mounting jig, 143: side swivel joint, 146: side load cell, 148: side rod
150: side load spring
170: wheel drive unit, 171: wheel driver, 173: wheel shaft, 177: wheel shaft support, 177a: load spindle, 177b: lower support
190: linear moving guide, 191: guide block, 192: side drive plate, 194: side guide rail, 196; Load drive plate, 198: Load guide rail
210: wheel drive plate, 410: rail drive plate
500: baseplate

Claims (6)

A load load that imparts a radial load to the wheel specimen in a radial direction of the wheel specimen, a side load that is disposed on one side of the wheel shaft to impart a thrust load to the wheel specimen, and the wheel specimen And a wheel shaft mounted thereon and a wheel driver for rotating the wheel specimen by rotating the wheel shaft, wherein the load load, the side load and the wheel driver are mounted on an upper portion of the wheel drive plate. Wheel specimen driving unit for applying a load; And,
A rail specimen driving unit having a rail shaft to which the rail specimen is coupled and a rail driving unit to rotate the rail shaft, the rail specimen driving unit being separately disposed with the wheel specimen driving unit parallel to the wheel shaft;
Includes a plurality of coil springs that can be adjusted in number of the elastic member for removing the high-frequency components of the load is installed in the axial direction to which the load is applied at one or more of the load load and the side load;
The elastic member
A first support plate on which a plurality of first fixing tubes are formed;
A second support plate on which a plurality of second fixing tubes are formed;
It includes; a plurality of coil springs of which the number is adjusted,
The first fixing tube and the second fixing tube are coupled to each other so that the coil spring is coupled to the outer periphery of the first fixing tube and the second fixing tube coupled to each other so as to be deformable in length and inserted into one another. And both ends of the coil spring are coupled to each other so as to be elastically supported by the first support plate and the second support plate, respectively. The method of claim 1, wherein the load load,
Swivel joint fixed to the mounting jig; And,
An actuator having one end coupled to the swivel joint;
A load detector coupled to the other end of the actuator;
And a load rod having one end coupled to an opposite end of the end coupled to the actuator of the elastic member and the other end coupled to a lower support of the wheel driving unit.
The elastic member is a wheel and rail testing apparatus for a railway vehicle, characterized in that installed in the region between any one of the actuator, the load detection unit and the load rod. The method of claim 1, wherein the side load,
Mounting jig;
A swivel joint fixed to the mounting jig;
An actuator coupled to the swivel joint; and
A load detector coupled to the other end of the end to which the swivel joint of the actuator is coupled;
And a side rod coupled to the opposite end of the end axially coupled to the load detection unit on one side in the axial direction, and the other end coupled to the wheel driving unit.
The elastic member is a wheel and rail test apparatus of the railway vehicle, characterized in that installed in the region between any one of the actuator, the load detection unit and the side rod. delete The method of claim 1, wherein the wheel driving unit,
At least one spindle rotatably supporting the wheel shaft; and
Wheel and rail test apparatus of the railway vehicle, characterized in that it further comprises a wheel shaft support configured to include; the lower support is detachably installed and the load rod of the load load (rod) is coupled. The method of claim 1, wherein the rail specimen drive unit,
A plurality of spindles rotatably supported by the rail shaft;
And a rail support base comprising: a vertical support attached to the bottom of the spindle so that the spindle is detachable.

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