Wheel testing device

Abstract

An embodiment of the present application provides a wheel testing device including: a track wheel support portion rotatably supporting a track wheel; a wheel support portion supporting a test wheel in a rotatable state in contact with the track wheel; a first motor rotating the track wheel and the test wheel; and a torque generating device generating a torque imparted to the test wheel, the torque generating device including: a rotating frame rotatably driven by a rotation driving device; and a second motor mounted to the rotating frame, at least one of the track wheel and the test wheel being connected to the first motor via the torque generating device.

Description

Technical Field

[0001] This invention relates to a wheel testing device. Background Technology

[0002] Test apparatuses for simulating the interaction between the track and wheels when a railway vehicle is in motion are known. For example, Japanese Patent Application Publication No. 2007-271447 (Patent Document 1) describes a test apparatus in which, by rotating the wheel and pressing it against a track wheel with a disc-shaped component having a cross-sectional shape simulating the track on its outer periphery, a test simulating the motion of a railway vehicle can be performed. Summary of the Invention

[0003] The testing device described in Patent Document 1 is driven by a single electric motor. Therefore, when performing tests that cause the wheels to rotate at high speed and impart high torque, a large-capacity electric motor is required, which leads to a significant increase in power consumption during testing.

[0004] The present invention is proposed in view of the above circumstances, and its purpose is to reduce the power consumption of the wheel testing device.

[0005] One embodiment of the present invention provides a wheel testing apparatus, comprising: a track wheel support portion rotatably supporting a track wheel; a wheel support portion that supports a test wheel in a rotatable manner while in contact with the track wheel; a first electric motor for rotating the track wheel and the test wheel; and a torque generating device for generating torque to the test wheel, the torque generating device comprising: a rotating frame rotatably driven by a rotation drive device; and a second electric motor mounted on the rotating frame, wherein at least one of the track wheel and the test wheel is connected to the first electric motor via the torque generating device.

[0006] The wheel testing device may also be configured to include a power distribution mechanism that distributes the power generated by the first electric motor to the track wheel and the test wheel.

[0007] The wheel testing device can also be configured such that when the second motor stops operating, the track wheel and the test wheel rotate in opposite directions at approximately the same circumferential speed.

[0008] The wheel testing device may also be configured such that the torque generating device has an output shaft coaxially configured with the rotating frame.

[0009] The wheel testing device may also be configured such that the torque generating device has a bearing unit that rotatably supports a rotating frame. The rotating frame has a cylindrical shaft portion supported by the bearing unit, and a bearing is provided on the inner circumference of the shaft portion. The output shaft is rotatably supported by the bearing through the hollow portion of the shaft portion.

[0010] The wheel testing device can also be configured such that the first motor and the rotating frame are coaxially arranged.

[0011] The wheel testing device may also be configured such that the second motor is fixed to the rotating frame via a plurality of rod-shaped connecting parts arranged radially around the rotating shaft of the rotating frame.

[0012] The wheel testing device may also be configured such that the rotating frame has a cylindrical motor housing for housing the second motor.

[0013] The wheel testing device may also be configured to include: a control unit for controlling a first motor and a second motor; a speed measuring mechanism for measuring the speed of the track wheel; and a torque measuring mechanism for measuring the torque of the test wheel. The control unit controls the drive of the first motor based on the measurement results of the speed measuring mechanism, and controls the drive of the second motor based on the measurement results of the torque measuring mechanism.

[0014] The wheel testing device may also be configured to include a wheel weight application unit, which applies wheel weight to the test wheel by moving one of the test wheel and the track wheel forward or backward relative to the other.

[0015] The wheel testing device may also be configured to include an attack angle imparting unit, which imparts an attack angle by rotating one of the test wheel and the track wheel relative to the other about a straight line perpendicular to the tread surface of the test wheel.

[0016] The wheel testing device may also be configured to include a cant angle imparting unit, which imparts a cant angle by rotating one of the test wheel and the track wheel about a tangent relative to the other.

[0017] The wheel testing device may also be configured to include a lateral pressure application unit, which applies lateral pressure to the test wheel by moving one of the test wheel and the track wheel axially relative to the other.

[0018] By employing the embodiments of the present invention, the power consumption of the wheel testing device can be reduced. Attached Figure Description

[0019] Figure 1 This is a perspective view of the wheel testing device according to the first embodiment of the present invention.

[0020] Figure 2 This is a perspective view of the wheel testing device according to the first embodiment of the present invention.

[0021] Figure 3 This is a top view of the wheel testing device according to the first embodiment of the present invention.

[0022] Figure 4 It is a block diagram representing the general structure of the drive system.

[0023] Figure 5 It is a cross-sectional view showing the general structure of the gearbox.

[0024] Figure 6 It is a cross-sectional view showing the general structure of the torque generating device and its surroundings.

[0025] Figure 7 This is a cross-sectional view showing the general structure of the second electric motor.

[0026] Figure 8 It is a block diagram that represents the general structure of the control system.

[0027] Figure 9 This is a top view showing the schematic structure of the wheel testing device according to the second embodiment of the present invention.

[0028] Figure 10 This is a front view showing the schematic structure of the wheel testing device according to the second embodiment of the present invention. Detailed Implementation

[0029] Hereinafter, embodiments of the present invention will be described with reference to the accompanying drawings. Furthermore, in the following description, identical or corresponding items will be labeled with the same or corresponding reference numerals, and repeated descriptions will be omitted. Additionally, when items shared by multiple reference numerals are shown in the figures, not all of the multiple items will be labeled with reference numerals; instead, some of the items will be appropriately omitted.

[0030] (First Implementation)

[0031] Figure 1 and Figure 2 These are perspective views of the wheel testing device 1 according to the first embodiment of the present invention. Figure 1 This is a picture viewed from the side from the front. Figure 2 This is a picture viewed from the back side. Figure 3 This is a top view of wheel testing device 1.

[0032] Figure 1 In this coordinate system, as shown by the coordinate axes, the direction from bottom right to top left is defined as the X-axis, the direction from top right to bottom left as the Y-axis, and the direction from bottom to top as the Z-axis. The X-axis and Y-axis are horizontal directions orthogonal to each other, while the Z-axis is vertical. Any straight line extending in each of the X-axis, Y-axis, and Z-axis directions is called the X-axis, Y-axis, and Z-axis, respectively. Furthermore, the positive X-axis direction is called left, the negative X-axis direction is called right, the positive Y-axis direction is called front, the negative Y-axis direction is called back, the positive Z-axis direction is called top, and the negative Z-axis direction is called bottom.

[0033] The wheel testing device 1 is a device that simulates the interaction between the track and the wheel during the movement of a railway vehicle, and can evaluate, for example, the adhesion characteristics between the track and the wheel. In this embodiment, a track wheel R with a cross-sectional shape simulating the head of a track is used. The interaction between the track and the wheel during the movement of a railway vehicle is simulated by rotating the track wheel R while pressing the wheel to be tested (hereinafter referred to as "test wheel W") against it.

[0034] The wheel testing device 1 includes a drive system DS for driving the track wheel R and the test wheel W. Figure 4 This is a block diagram showing the general structure of the drive system DS. The drive system DS includes: an engine AS that generates mechanical power (hereinafter referred to as "power"); and a transmission TS that transmits the power generated by the engine AS to the track wheel R and the test wheel W, which are the objects being driven, together with the track wheel R and the test wheel W, forming a power circulation system.

[0035] The engine unit AS includes: a rotation drive device 10 (speed control drive device) for controlling the rotational speed of the driven object; and a torque generating device 20 (torque control drive device) for controlling the torque applied to the driven object. The drive system DS of this embodiment, by employing a structure that divides drive control into speed control and torque control, with each dedicated drive device handling both speed and torque control, enables high-speed (or high-acceleration) and high-torque drive while using a relatively small-capacity engine. Furthermore, by employing a power cycle system, the drive system DS achieves higher energy utilization efficiency than existing devices.

[0036] The transmission unit TS includes a first transmission unit 30 and a second transmission unit 40. Furthermore, the torque generating device 20 also forms part of the transmission unit TS. The first transmission unit 30 transmits the rotation output from the rotary drive unit 10 to the track wheel R and the torque generating device 20. The torque generating device 20 outputs power after adding its own power to the power transmitted from the rotary drive unit 10. The second transmission unit 40 transmits the output of the torque generating device 20 to the test wheel W.

[0037] The track wheel R and the test wheel W are mounted radially in the wheel testing device 1, parallel to each other in the orientation of their rotation axes. During testing, the test wheel W is pressed against the track wheel R. With the outer circumferential surface (tread) of the test wheel W in contact with the outer circumferential surface (top surface) of the track wheel R, the test wheel W and the track wheel R rotate in opposite directions at approximately the same circumferential speed (i.e., the linear velocity of their outer circumferential surfaces). At this time, the transmission unit TS, together with the test wheel W and the track wheel R, constitutes a power circulation system (i.e., a loop of power transmission shafts). The torque generating device 20 applies torque to the power circulation system by imparting a phase difference between the input shaft (first transmission unit 30) and the output shaft (second transmission unit 40). By employing a power circulation method, the wheel testing device 1 can apply torque (or tangential force) to the test wheel W with almost no absorption of the generated power, thus enabling operation with relatively low energy consumption.

[0038] Furthermore, in this embodiment, the first transmission unit 30 is configured to drive the track wheel R and the test wheel W to rotate in opposite directions at the same circumferential speed when the torque generating device 20 (specifically, the second electric motor 22 described later) is stopped. Alternatively, it can be configured such that a difference in circumferential speed exists between the track wheel R and the test wheel W when the torque generating device 20 is stopped. However, in this case, the actuation amount of the torque generating device 20 increases to compensate for the difference in circumferential speed, thus increasing energy consumption. Furthermore, while the first transmission unit 30 in this embodiment is configured to drive the track wheel R and the torque generating device 20 to rotate at the same speed, any structure that drives the track wheel R and the test wheel W to rotate at approximately the same circumferential speed can also be configured to allow the track wheel R and the torque generating device 20 to rotate at different speeds.

[0039] like Figure 1-3 As shown, the rotary drive unit 10 includes: a tension adjustment table 11; and a first motor 12 (speed control motor) mounted on the tension adjustment table 11. In this embodiment, the first motor 12 is a so-called inverter motor that is controlled and driven by an inverter; however, other types of motors with controllable speeds, such as servo motors or stepper motors, may also be used for the first motor 12. Furthermore, the rotary drive unit 10 may also include a speed reducer that reduces the rotation output from the first motor 12. The tension adjustment table 11 will be described later.

[0040] The first transmission unit 30 includes: a first belt mechanism 31, a track wheel support 32, a shaft 33, and a gearbox 34 (gear assembly).

[0041] like Figure 1As shown, the first belt mechanism 31 includes: a drive pulley 311 driven by a rotary drive device 10; a driven pulley 312 mounted on the input shaft (one of the shaft 321 described later) of the track wheel support 32; and a belt 313 wound on the drive pulley 311 and the driven pulley 312.

[0042] The rotation output from the rotary drive device 10 is transmitted to the track wheel support 32 via the first belt mechanism 31 of the first transmission unit 30.

[0043] The belt 313 in this embodiment is a V-rib belt having a plurality of V-shaped ribs arranged in the width direction, but it may also be other types of belts such as V-shaped belts with trapezoidal cross-sections, toothed belts, flat belts, and round belts.

[0044] The first belt drive unit 31 in this embodiment includes a single belt drive unit consisting of a drive pulley 311, a driven pulley 312 and a belt 313, but it may also include two or more belt drive units connected in parallel or in series.

[0045] Furthermore, when transmitting power from the rotary drive 10 to the track wheel support 32, it is not limited to belt drive; other types of transmission methods, such as chain drive, wire drive, or gear drive, can also be used. Additionally, the rotary drive 10 and the track wheel support 32 can be configured coaxially (i.e., with their rotation axes or center lines aligned), with the output shaft of the rotary drive 10 directly connected to the input shaft of the track wheel support 32.

[0046] The tension adjustment table 11 of the rotary drive device 10 is described here. For example... Figure 2 As shown, the tension adjustment table 11 includes: a fixed frame 111 fixed to the base B; and a movable frame 112 on which the rotary drive device 10 is mounted. The movable frame 112 is rotatably connected to the fixed frame 111 at its right end via a rod 114R extending in the Y-axis direction, allowing adjustment of its tilt about the Y-axis. By changing the tilt of the movable frame 112, the drive pulley 311 ( Figure 1 The distance between the drive pulley 311 and the driven pulley 312 changes, thereby adjusting the tension of the belt 313 wound between the drive pulley 311 and the driven pulley 312.

[0047] like Figure 2 and Figure 3 As shown, the track wheel support 32 includes a pair of bearings 322 and a shaft 321. The pair of bearings 322 oriented the rotation axis toward the Y-axis, sandwiching the track wheel R in the middle and arranging them front and back (i.e., in the Y-axis direction) and coaxially configured.

[0048] One shaft 321 is rotatably supported by a front bearing 322, and the other shaft 321 is rotatably supported by a rear bearing 322. The shaft 321 is a flanged shaft with a flange at one end for mounting a track wheel R, and is detachably and coaxially mounted to the two sides of the track wheel R by a single bolt.

[0049] A driven pulley 312 of the first belt mechanism 31 is mounted at the other end of the front shaft 321. Furthermore, one end of a shaft 33 is connected to the other end of the rear shaft 321. The other end of the shaft 33 is connected to the input shaft 342a of the gearbox 34.

[0050] A portion of the power transmitted from the first belt mechanism 31 to the track wheel support 32 is given to the track wheel R, and the remainder is given to the shaft 33 (and then, via the shaft 33, the torque generating device 20, and the second transmission unit 40, to the test wheel W). That is, the track wheel support 32 (specifically the shaft 321) functions as a power distribution mechanism that distributes the power generated by the first motor 12 and transmitted by the first belt mechanism 31 to the track wheel R and the shaft 33 (and ultimately to the test wheel W).

[0051] Furthermore, the connection between the shaft 321 and the track wheel R is not limited to the use of a flange connection. For example, it can also be other connection structures such as the shaft 321 being fitted into a through hole provided in the center of the track wheel R.

[0052] In addition, such as Figure 3 As shown, the track wheel support 32 includes a rotary encoder 323 (speed detection mechanism) for detecting the rotational speed of the track wheel R.

[0053] Figure 5 This is a schematic cross-sectional view of the gearbox 34 and its periphery cut off in a horizontal plane. The gearbox 34 includes: a housing 341; a pair of first bearings 343 and a pair of second bearings 345 mounted on the housing 341; a first gear 342 (input-side gear) rotatably supported by the pair of first bearings 343; and a second gear 344 (output-side gear) rotatably supported by the pair of second bearings 345.

[0054] The first gear 342 and the second gear 344 are arranged in the X-axis direction with their rotation axes facing the Y-axis and their teeth meshing with each other, and are housed in the housing 341. One end of the first gear 342 is the input shaft 342a of the gearbox 34, which is connected to the other end of the shaft 33. The flange formed at one end of the second gear 344 is the output shaft 344a of the gearbox 34, which is connected to the flange (input shaft 211b) formed at one end of the housing 21 of the torque generating device 20 (described later).

[0055] The second gear 344 has a cylindrical through hole 344b with the rotation axis as its center line. The output shaft 24 of the torque generating device 20, described later, extends from one end of the second gear 344. Figure 5 The left end of the output shaft 344a is inserted into the through hole 344b, passing through the second gear 344, with its front end protruding from the other end of the second gear 344.

[0056] In this embodiment, the first gear 342 and the second gear 344 have the same number of teeth, and the gear ratio of the gearbox 34 is 1. Alternatively, as long as the structure causes the test wheel W and the track wheel R to rotate in opposite directions at approximately the same circumferential speed, the gear ratio of the gearbox 34 can be a value other than 1.

[0057] When the transmission from shaft 33 to torque generating device 20 is not limited to gear transmission, other transmission methods such as belt transmission or chain transmission can also be used.

[0058] Figure 6 This is a schematic cross-sectional view of the torque generating device 20 and gearbox 34 and their surroundings cut off in a plane perpendicular to the X-axis direction.

[0059] The torque generating device 20 includes: a main body 20A (rotating part) that is driven by a rotary drive device 10; and a pair of bearing units 25, 26 that rotatably support the main body 20A.

[0060] The main body 20A includes: a generally cylindrical housing 21 (rotating frame) supported by bearing units 25 and 26; a second motor 22 and a reducer 23 mounted on the housing 21; and an output shaft 24. The output shaft 24 is coaxially arranged with the housing 21. Alternatively, the shaft 221 and rotor 222 of the second motor 22 (described later) can be coaxially arranged with the housing 21. By coaxially arranging the second motor 22 with the housing 21, the imbalance of the main body 20A is reduced, allowing the main body 20A to rotate smoothly (i.e., reducing unnecessary wobbling of speed and torque). In addition, the second motor 22 in this embodiment is an AC servo motor, but other types of motors with controllable drive amount (rotation angle), such as DC servo motors and stepper motors, can also be used as the second motor 22. In this embodiment, the rotational inertia of the rotating part used as the second motor 22 is 0.01 kg·m. 2 The following (more preferably 0.008 kg·m) 2 The following are ultra-low inertia, high-power AC servo motors with rated power ranging from 3kW to 60kW (7kW to 37kW for more practical applications). This allows for the generation of rapid torque variations (e.g., high-frequency vibration torque exceeding 500Hz or 1kHz).

[0061] The housing 21 has: a generally cylindrical first cylindrical portion 212 and a generally cylindrical second cylindrical portion 214 (motor housing); a connecting portion 213 connecting the first cylindrical portion 212 and the second cylindrical portion 214; a first shaft portion 211 connected to the first cylindrical portion 212; and a second shaft portion 215 connected to the second cylindrical portion 214. The first shaft portion 211, the first cylindrical portion 212, the connecting portion 213, the second cylindrical portion 214, and the second shaft portion 215 are all cylindrical components with a hollow portion extending axially, and are coaxially connected in this order to form the cylindrical housing 21. The housing 21 is supported by a bearing unit 25 at the first shaft portion 211 and by a bearing unit 26 at the second shaft portion 215. The flange formed at the front end of the first shaft portion 211 is the input shaft 211b of the torque generating device 20. Figure 5 ), connected to the output shaft 344a of the gearbox 34.

[0062] Figure 7 This is a longitudinal cross-sectional view showing the schematic structure of the second motor 22. The second motor 22 includes: a shaft 221; a rotor 222 integrally formed with the shaft 221 and composed of permanent magnets, etc.; a cylindrical stator 223 with coils 223a arranged on its inner circumference; a pair of flanges 224, 226 mounted at both ends of the stator 223 by means of blocking openings; a pair of bearings 225, 227 mounted on each flange 224, 226; and a rotary encoder RE for detecting the angular position (phase) of the shaft 221.

[0063] Shaft 221 is rotatably supported by a pair of bearings 225, 227. One end of shaft 221 ( Figure 7 The right end of the shaft 221 (through flange 224 and bearing 225) protrudes outward to become the output shaft of the second motor 22. The other end of the shaft 221 ( Figure 7 The left end of the component is connected to the rotary encoder RE.

[0064] like Figure 6 As shown, the second motor 22 is housed in the hollow portion (section C1) of the second cylindrical portion 214 of the housing 21. At one end of the connecting portion 213 of the housing 21 ( Figure 6 The left end of the middle) has an inner flange portion 213a that protrudes inward. The stator 223 of the second motor 22 ( Figure 7 The second motor 22 is fixed to the second cylindrical portion 214 via a plurality of rod-shaped connecting members 217 arranged radially around the rotation axis of the torque generating device 20. The connecting members 217 can be, for example, stud bolts or fully threaded bolts with male threads at both ends. Furthermore, the flange 224 of the second motor 22 ( Figure 7 It is supported by the inner flange 213a of the connecting part 213.

[0065] The reducer 23 is housed in partition C2, which is surrounded by the connecting portion 213 of the housing 21 and the first cylindrical portion 212. The input shaft 231 of the reducer 23 is connected to the shaft 221 of the second motor 22, and the output shaft 232 of the reducer 23 is connected to the output shaft 24 of the torque generating device 20. Alternatively, the reducer 23 may not be installed in the torque generating device 20, and the output shaft 24 may be directly connected to the shaft 221 of the second motor 22.

[0066] The housing 233 of the reducer 23 is fixed to the other end of the connecting part 213. That is, the flange 224 of the second motor 22 ( Figure 7 The housing 233 of the second motor 22 and the reducer 23 are integrally connected by a single cylindrical connecting part 213. Therefore, the second motor 22 and the reducer 23 are integrally joined with high rigidity, making it less likely to exert bending torque on the shaft 221. This reduces the stress on the shaft 221 caused by bearings 225 and 227. Figure 7 The friction it experiences improves the accuracy of torque control performed by the torque generating device 20.

[0067] The output shaft 24 of the torque generating device 20 passes through the hollow portion of the first shaft portion 211 of the housing 21 and the gearbox 34 (specifically, the second gear 344), and protrudes towards the rear of the gearbox 34. Bearings 211a and 344c, which rotatably support the output shaft 24, are respectively provided on the inner circumference of the first shaft portion 211 of the housing 21 and the second gear 344 of the gearbox 34.

[0068] Two drive pulleys 411 of the second belt mechanism 41 (described later) are mounted on the front end of the output shaft 24, which protrudes rearward from the gearbox 34. Furthermore, the front end of the output shaft 24 is rotatably supported by the bearing unit 414 of the second belt mechanism 41.

[0069] Adjacent to the front of bearing unit 26 ( Figure 6 A slip ring 27 is provided on the left side. The slip ring 27 consists of a movable part 27A that rotates together with the main body 20A of the torque generating device 20, and a fixed part 27B that is fixed to the base B.

[0070] The movable part 27A includes: a ring support tube 271 coaxially connected to the second shaft part 215 of the torque generating device 20; and a plurality of slip rings 272 axially spaced apart and coaxially mounted on the outer periphery of the ring support tube 271.

[0071] The cable 228 of the second motor 22 of the torque generating device 20 passes through the second shaft portion 215 of the housing 21. Furthermore, multiple wires constituting the cable 228 are connected to corresponding slip rings 272 through the hollow portion of the ring support tube 271.

[0072] The fixing part 27B includes: a brush support part 274; a plurality of brushes 273 supported by the brush support part 274; and a bearing part 275 that rotatably supports the front end of the ring support tube 271. The brushes 273 are arranged at intervals in the Y-axis direction in such a way that they contact the outer peripheral surface of the corresponding slip rings 272. The brushes 273 are wired to the servo amplifier 22a, etc., which will be described later.

[0073] A rotary encoder 28 is installed in the bearing section 275 to detect the rotational speed of the ring support tube 271 (i.e., the rotational speed of the housing 21, which serves as the input shaft of the torque generating device 20).

[0074] like Figure 3 As shown, the second transmission unit 40 includes: a second belt mechanism 41, a sliding constant velocity joint 42, and a wheel support 50.

[0075] The second belt mechanism 41 includes: two sets of belt drive units consisting of a drive pulley 411, a driven pulley 412 and a belt 413; a bearing unit 414; a shaft 415; and a pair of bearing units 416.

[0076] As described above, two drive pulleys 411 are respectively mounted on the front end of the output shaft 24 of the torque generating device 20 passing through the gearbox 34. In addition, the bearing unit 414 rotatably supports the front end of the output shaft 24.

[0077] Alternatively, an additional bearing unit 414 can be provided between the gearbox 34 and the drive pulley 411, with one pair of bearing units 414 supporting the front end of the output shaft 24. Furthermore, in this embodiment, the drive pulley 411 is directly mounted on the output shaft 24 of the torque generating device 20; however, it is also possible to provide a separate shaft supporting the drive pulley 411 in addition to the output shaft 24, with the bearing unit 414 supporting this shaft connected to the output shaft 24.

[0078] Two driven pulleys 412 are mounted on a shaft 415 which is rotatably supported by a pair of bearing units 416.

[0079] Belt 413 is wound around the corresponding drive pulley 411 and driven pulley 412.

[0080] The belt 413 in this embodiment is a toothed belt with a steel wire core. Alternatively, belts with cores formed of so-called microfibers, such as carbon fiber, aramid fiber, or ultra-high molecular weight polyethylene fiber, can also be used as belt 413. By using lightweight and high-strength cores such as carbon fiber cores, it is possible to drive the wheel W with high acceleration using a lower-power motor (or to impart high driving / braking force), thus miniaturizing the wheel testing device 1. Furthermore, when using a motor of the same power, the wheel testing device 1 can be performed with high performance by using a lightweight (i.e., low-inertia) belt 413 with a core formed of so-called microfibers. Alternatively, a general automotive or industrial timing belt can be used as belt 413. Furthermore, a flat belt or V-belt can be used instead of a toothed belt as belt 413. Additionally, the belt 313 of the first belt mechanism 31 can also be any of these belts that can be used as belt 413.

[0081] The second belt mechanism 41 in this embodiment includes a pair of belt drive units connected side by side, but it may also be configured to include a single or three or more belt drive units connected side by side.

[0082] Furthermore, when transmitting power from the torque generating device 20 to the sliding constant velocity joint 42, it is not limited to belt drive; other types of transmission methods such as chain drive, wire drive, or gear drive can also be used. Additionally, the torque generating device 20 and the sliding constant velocity joint 42 can be arranged in a generally straight line (or U-shape), directly connecting the output shaft 24 of the torque generating device 20 to the input shaft of the sliding constant velocity joint 42.

[0083] The wheel support 50 is connected to the torque generating device 20 via a sliding constant velocity joint 42. Specifically, one end of the sliding constant velocity joint 42 (i.e., the input shaft) is connected to the shaft 415 of the second belt mechanism 41, and the other end of the sliding constant velocity joint 42 (the output shaft) is connected to the spindle 527 of the wheel support 50, which will be described later.

[0084] The sliding constant velocity joint 42 is configured to smoothly transmit rotation without rotational variation regardless of the working angle (i.e., the angle between the input shaft and the output shaft). Furthermore, the axial length (transmission distance) of the sliding constant velocity joint 42 is also variable.

[0085] As described below, the spindle 527 is supported in a position-variable manner. By connecting the spindle 527 to the shaft 415 of the second belt mechanism 41 (or the output shaft 24 of the torque generating device 20) via a sliding constant velocity joint 42, even if the position of the spindle 527 changes, the sliding constant velocity joint 42 flexibly follows the change, thus preventing large strain on the spindle 527 and the shaft 415 (or the output shaft 24 of the torque generating device 20), and smoothly transmitting rotation to the spindle 527. Furthermore, by using the sliding constant velocity joint 42, changes in the rotational speed transmitted to the spindle 527 due to the position of the spindle 527 (or the operating angle of the sliding constant velocity joint 42) can be prevented.

[0086] like Figure 1 As shown, the wheel support 50 includes: a fixed base 51; and a main body 52 and a wheel weight imparting part 53 disposed on the fixed base 51.

[0087] like Figure 3 As shown, the main body 52 includes: a movable base 522; a pair of linear guides 521 that movably support the movable base 522 in the X-axis direction relative to the fixed base 51; a support frame 523 disposed on the movable base 522; a bearing unit 528 mounted on the support frame 523; a spindle 527 rotatably supported by the bearing unit 528; a torque sensor 524 and a detection gear 525 coaxially mounted on the spindle 527; and a rotation detector 526 for detecting the rotation of the detection gear 525. The linear guide 521 is a guide-shaped circulating rolling bearing comprising a straight guideway and a carriage that can travel on the guideway via a rotating body, but other linear guide mechanisms may also be used as the linear guide 521. The linear guide 521 forms part of the wheel weight imparting part 53. Furthermore, the detection gear 525 and the rotation detector 526 constitute a rotational speed detection mechanism for detecting the rotational speed of the spindle 527.

[0088] The support frame 523 has a support column 523a fixed to the movable base 522, and an arm 523b fixed to the support column 523a. In this embodiment, the support column 523a is an L-shaped bracket, but other forms of support column 523a can also be used. Furthermore, the support column 523a and arm 523b can be integrally formed. The arm 523b is a generally L-shaped structure when viewed from above, having a base 523b1 extending rearward from the upper part of the support column 523a, and a main body 523b2 extending to the left from the rear end of the base 523b1. A hollow portion extending through the Y-axis is formed at the front end of the main body 523b2. This hollow portion allows the drive shaft (specifically, a structure connecting the sliding constant velocity joint 42, torque sensor 524, detection gear 525, and spindle 527) to pass through.

[0089] Bearing unit 528 is mounted on arm 523b. Specifically, bearing unit 528 is mounted on the front side of the front end of main body 523b2 with the rotation axis facing the Y-axis. Multiple three-component sensors 529 (tangential force detection mechanism, first transverse pressure detection mechanism) are provided in bearing unit 528 to detect the force exerted on spindle 527. The three-component sensors 529 are piezoelectric force sensors, but other types of force sensors can also be used as three-component sensors 529.

[0090] The spindle 527 is connected to the output shaft of the sliding constant velocity joint 42 via a detection gear 525 and a torque sensor 524. The detection gear 525 and the torque sensor 524 are housed in a hollow portion formed at the front end of the main body 523b2. The test wheel W is mounted on a mounting portion provided at the front end of the spindle 527. The torque sensor 524 detects the torque applied to the spindle 527 (i.e., applied to the test wheel W).

[0091] The rotary detector 526 is configured opposite to the outer peripheral surface of the detection gear 525 and is fixed to the main body 523b2 of the support frame 523. The rotary detector 526 is a non-contact rotary detector, such as an optical, electromagnetic, or magnetoelectric type, used to detect changes in the angular position of the detection gear 525.

[0092] The wheel weight imparting part 53 is a mechanism that moves the main body 52 of the wheel support part 50 in the X-axis direction and imparts a specified wheel weight to the test wheel W by pressing the test wheel W mounted on the spindle 527 against the track wheel R.

[0093] The wheel weight application unit 53 includes: a motor 531; a motion converter 532 that converts the rotational motion of the motor 531 into linear motion in the X-axis direction; and a wheel weight detector 533 that detects the wheel weight applied to the test wheel W. Figure 10 ).

[0094] Motor 531 is an AC servo motor, but other types of motors with controllable drive amount (rotation angle), such as DC servo motors or stepper motors, can also be used as motor 531.

[0095] The motion converter 532 in this embodiment is, for example, a screw jack that combines a reducer such as a worm gear device with a feed screw mechanism such as a ball screw, but other types of motion converters may also be used. The linear motion part 532a of the motion converter 532 is fixed to the support frame 523 via a wheel weight detector 533.

[0096] When the motion converter 532 is driven by the motor 531, the support frame 523 and the spindle 527 supported on the support frame 523 move together with the linear motion unit 532a in the X-axis direction. At the same time, the test wheel W mounted on the spindle 527 moves forward and backward relative to the track wheel R. When the test wheel W is in contact with the track wheel R, and the motion converter 532 is further driven by the motor 531 in the direction that moves the test wheel W toward the track wheel R (i.e., the positive X-axis direction), the test wheel W is pressed against the track wheel R, and a wheel weight is assigned to the test wheel W.

[0097] The wheel weight detector 533 is a force sensor that detects the force (i.e., wheel weight) applied to the test wheel W in the X-axis direction via the wheel weight application unit 53, support frame 523, and spindle 527. In this embodiment, the wheel weight detector 533 is a strain gauge load sensor, but other types of force sensors, such as piezoelectric force sensors, can also be used as the wheel weight detector 533. The control unit 70, described later, controls the drive of the motor 531 to apply a predetermined wheel weight to the test wheel W based on the detection result of the wheel weight detector 533.

[0098] Figure 8 This is a block diagram showing the general structure of the control system CS of the wheel testing device 1. The control system CS includes: a control unit 70 that controls the overall operation of the wheel testing device 1; a measurement unit 80 that performs various measurements based on signals from various detectors installed on the wheel testing device 1; and an interface unit 90 that performs input and output to the outside.

[0099] The control unit 70 is connected to the second motor 22 and the motor 531 via servo amplifiers 22a and 531a respectively, and the first motor 12 is connected via driver 12a (inverter circuit).

[0100] The measuring unit 80 is connected to rotary encoders 28 and 323, torque sensor 524, three-component force sensor 529, and wheel weight detector 533 via amplifiers 28a, 323a, 524a, 529a, and 533a, respectively. Additionally, Figure 8 In this context, only one set of the multiple sets of three-component force sensors 529 and amplifiers 529a installed in the wheel testing device 1 is represented. Furthermore, the rotation detector 526, which has a built-in amplifier circuit and analog-to-digital conversion circuit, is directly connected to the measurement unit 80.

[0101] The measurement unit 80 measures the rotational speed of the track wheel R based on the signal of the rotary encoder 323, measures the rotational speed of the input shaft (housing 21) of the torque generating device 20 based on the signal of the rotary encoder 28, and measures the rotational speed of the spindle 527 (i.e., the rotational speed of the test wheel W) based on the signal of the rotary detector 526. Furthermore, the measurement unit 80 measures the torque applied to the test wheel W based on the signal from the torque sensor 524, measures the tangential force (longitudinal creep force) and lateral pressure (thrust load) applied to the test wheel W based on the signals from multiple three-component force sensors 529, and measures the wheel weight based on the signal from the wheel weight detector 533. That is, the measurement unit 80 functions as a first speed measuring mechanism for measuring the rotational speed of the track wheel R, a second speed measuring mechanism for measuring the rotational speed of the torque generating device 20, a third speed measuring mechanism for measuring the rotational speed of the test wheel W, a torque measuring mechanism for measuring the torque applied to the test wheel W, a tangential force measuring mechanism for measuring the tangential force applied to the test wheel W, a lateral pressure measuring mechanism for measuring the lateral pressure applied to the test wheel W, and a wheel weight measuring mechanism for measuring the wheel weight applied to the test wheel W. The measurement unit 80 transmits these measured values ​​to the control unit 70.

[0102] The wheel testing device 1 of this embodiment is a highly versatile device, so it includes many measuring mechanisms and corresponding testing mechanisms. However, the wheel testing device 1 does not need to include all of these measuring mechanisms and testing mechanisms. It only needs to have one or more measuring mechanisms and testing mechanisms appropriately selected according to the matters to be investigated through the test.

[0103] The phase information of the shaft detected by the rotary encoder RE built into each servo motor (second motor 22, motor 531) is input to the control unit 70 via the corresponding servo amplifiers 22a and 531a.

[0104] The interface unit 90 includes, for example, a user interface for input / output with the user; a network interface for connecting to various networks such as LAN (Local Area Network); and one or more communication interfaces such as USB (Universal Serial Bus) and GPIB (General Purpose Interface Bus) for connecting to external devices. Furthermore, the user interface includes, for example, one or more input / output devices such as various operation switches, displays, LCD (liquid crystal display) and other display devices, various pointing devices such as mice and touchpads, touch screens, cameras, printers, scanners, buzzers, speakers, microphones, memory card readers and writers.

[0105] Based on the set data of the rotational speed (or circumferential speed) of the track wheel R input via the interface unit 90 and the measurement results of the rotational speed of the track wheel R by the measurement unit 80, the control unit 70 controls the drive of the first motor 12 so that the track wheel R rotates at the set speed.

[0106] Based on the wheel weight setting data input via the interface unit 90 and the wheel weight measurement results from the measurement unit 80, the control unit 70 controls the drive of the motor 531 of the wheel weight application unit 53, so that the set wheel weight is applied to the test wheel W.

[0107] Based on the torque setting data of the test wheel W input via the interface unit 90 and the torque measurement results of the test wheel W by the measurement unit 80, the control unit 70 controls the drive of the second motor 22 of the torque generating device 20 so that the set torque is applied to the test wheel W.

[0108] Next, an example of a testing method using the wheel testing device 1 will be described. First, with the track wheel R and the test wheel W installed in the wheel testing device 1, the control unit 70 drives the motor 531 of the wheel weight application unit 53 to bring the test wheel W close to the track wheel R and make contact with it, thus applying the set wheel weight to the test wheel W. Furthermore, the set value for the wheel weight can be a fixed value or a variable value that changes over time.

[0109] Next, the control unit 70 drives the first motor 12 of the rotary drive device 10 to rotate the track wheel R at a set speed. Furthermore, the set value for the speed of the track wheel R can be a fixed value or a variable value that changes over time. In addition, the control unit 70 controls the second motor 22 so that the torque of the test wheel W becomes zero (no load) until the speed of the track wheel R reaches the set value.

[0110] When the rotational speed of the track wheel R reaches the set value, the control unit 70 controls the drive of the second motor 22 of the torque generating device 20 to impart a set torque to the test wheel W. Furthermore, the set value for the torque of the test wheel W can be a fixed value or a variable value that changes over time. Alternatively, the drive of the second motor 22 can be controlled to impart a set torque to the test wheel W from the moment the track wheel R begins to rotate.

[0111] In this state, the control unit 70 continuously measures the rotational speed of the track wheel R, the torque, tangential force, lateral pressure, and wheel weight of the test wheel W during a predetermined time (test time), while rotating the track wheel R and the test wheel W. At this time, the control unit 70 stores each measured value in association with the measurement time in its storage device 71 (or, for example, in a storage mechanism accessible to the control unit 70 via a server connected to the control unit 70 via a LAN).

[0112] When the specified time has elapsed, the control unit 70 controls the drive of the second motor 22 of the torque generating device 20 to make the torque of the test wheel W zero. Next, the control unit 70 controls the first motor 12 of the rotation drive device 10 to gradually reduce the rotation speed of the track wheel R until it stops rotating, and then drives the motor 531 of the wheel weight transfer unit 53 to make the test wheel W move away from the track wheel R a specified distance to end the test.

[0113] Furthermore, the above test procedure is only one example of the test process that can be performed using the wheel test device 1, and various other test processes can also be used.

[0114] (Second Implementation)

[0115] Next, the second embodiment of the present invention will be described. Furthermore, in the following description of the second embodiment, the focus will be on aspects that differ from the first embodiment described above; structures common to or corresponding to those in the first embodiment will be labeled with the same or corresponding reference numerals, and repeated descriptions will be omitted.

[0116] Figure 9 This is a schematic top view showing the structure of the wheel testing apparatus 1000 according to the second embodiment of the present invention. Furthermore, Figure 10 This is a front view showing the general structure of the wheel testing device 1000.

[0117] The wheel testing device 1000 includes a wheel support 1500 that adds lateral pressure imparting function, attack angle imparting function and cant angle imparting function to the wheel support 50 of the first embodiment.

[0118] like Figure 9 As shown, the wheel support section 1500 of the wheel testing device 1000, in addition to the wheel weight imparting section 53, also includes a lateral pressure imparting section 54, a camber imparting section 55, and an angle of attack imparting section 56. Furthermore, as... Figure 10 As shown, the wheel support 1500 includes three movable bases (first movable base 522A, second movable base 522B and third movable base 522C).

[0119] The lateral pressure application unit 54 is a mechanism that applies lateral pressure (thrust load) to the test wheel W. Furthermore, the lateral pressure includes: lateral creep force (the axial component of the adhesive force on the test wheel W) and flange reaction force (the effect generated due to the contact between the flange of the test wheel W and the gauge corner of the track wheel R). The latter flange reaction force is applied by the lateral pressure application unit 54 (or adjusted to a predetermined value).

[0120] The transverse pressure imparting part 54 includes: a plurality (e.g., 3) of linear guides 541 that movably support the first movable base 522A in the Y-axis direction relative to the fixed base 51; and a motor 542 mounted together with the fixed base 51 on the base B. Figure 9 ); Motion converter 543 converts the rotational motion of motor 542 into linear motion in the Y-axis direction. Figure 9 ); and a lateral pressure detector 544 for detecting the lateral pressure applied to the test wheel W. Figure 9 Linear guide 541 is a guide rail-type circulating rolling bearing with the same structure as linear guide 521, but other linear guide mechanisms can also be used as linear guide 541.

[0121] In this embodiment, the lateral pressure detector 544 (second lateral pressure detection mechanism) is used to detect lateral pressure when a flange reaction force is applied, while the three-component force sensor 529 (first lateral pressure detection mechanism) is used to detect lateral pressure when no flange reaction force is applied. Alternatively, the wheel testing device 1000 may not include the lateral pressure detector 544, and the three-component force sensor 529 may be used to detect lateral pressure even when a flange reaction force is applied. Furthermore, the lateral pressure detector 544 may be used to detect lateral pressure when no flange reaction force is applied. Additionally, the lateral pressure detector 544 may be used to detect static lateral pressure (mainly flange reaction force), while the three-component force sensor 529 may be used to detect dynamic lateral pressure (mainly lateral creep force).

[0122] The motor 542 in this embodiment is an AC servo motor, but other types of motors with controllable drive amount (rotation angle), such as DC servo motors or stepper motors, can also be used as motor 542.

[0123] The motion converter 543 in this embodiment is a feed screw mechanism such as a ball screw, but other types of motion converters can also be used. The threaded shaft of the motion converter 543 is rotatably supported by a pair of bearings mounted on a fixed base 51, and one end is connected to the shaft of a motor 542. The nut (linear motion part) of the motion converter 543 is fixed to a first movable base 522A via a transverse pressure detector 544. When the threaded shaft of the motion converter 543 is rotated by the motor 542, the first movable base 522A and the nut of the motion converter 543 move together in the Y-axis direction. Consequently, the test wheel W supported on the first movable base 522A also moves in the Y-axis direction, and the axial position of the test wheel W relative to the track wheel R changes. When the test wheel W is displaced in the Y-axis direction, causing the flange of the test wheel W to contact the track wheel R, a flange reaction force is applied to the test wheel W. The magnitude of the flange reaction force varies depending on the position of the test wheel W in the Y-axis direction.

[0124] like Figure 8As shown, motor 542 is connected to control unit 70 via servo amplifier 542a. Horizontal pressure detector 544 is connected to measurement unit 80 via amplifier 544a. Additionally, the phase information of the shaft detected by the rotary encoder RE built into motor 542 is input to control unit 70 via servo amplifier 542a.

[0125] The measuring unit 80 measures the lateral pressure applied to the test wheel W based on the signal from the lateral pressure detector 544. The control unit 70 controls the drive of the motor 542 based on the lateral pressure setting data input via the interface unit 90 and the lateral pressure measurement results from the measuring unit 80, so that the set lateral pressure is applied to the test wheel W.

[0126] The tilt angle imparting part 55 is a mechanism that imparts a tilt angle to the test wheel W. For example... Figure 10 As shown, the tilting angle imparting part 55 includes: a vertically extending rotary support shaft 551 mounted on one of the first movable base 522A and the second movable base 522B; and a bearing 552 rotatably supporting the rotary support shaft 551 and mounted on the other of the first movable base 522A and the second movable base 522B. The second movable base 522B is rotatably supported by the rotary support shaft 551 and the bearing 552 with the rotation axis A1 of the bearing 552, which is a vertical line, as the center.

[0127] The bearing 552 is positioned approximately directly below the contact position P, with the test wheel W contacting the track wheel R via the rotation axis A1 at the contact position P (in this embodiment, the right end of the track wheel R). The rotation axis A1 forms a tangent to both the track wheel R and the test wheel W at the contact position P. Therefore, when the second movable base 522B rotates around the rotation axis A1, the test wheel W rotates around the Z-axis with the contact position P as a fulcrum (in other words, it rotates and moves around the tangent shared by the test wheel W and the track wheel R), changing its inclination (i.e., cant angle) relative to the tangent of the track wheel R.

[0128] The tilting section 55 includes a curved guide 553 that rotatably supports the second movable base 522B on its outer periphery, away from the rotation axis A1, relative to the first movable base 522A about the rotation axis A1. The curved guide 553 is a guide rail-shaped circulating rolling bearing that includes a curved track (guide rail) and a carriage that can travel on the track via a rotating body, but other curved guiding mechanisms may also be used as the curved guide 553.

[0129] In addition, the tilting unit 55 includes: a motor 554 ( Figure 9The system includes a motion converter 555 that converts the rotational motion of motor 554 into linear motion in the Y-axis direction. In this embodiment, motor 554 is an AC servo motor, but other types of motors with controllable drive quantity (rotation angle), such as DC servo motors or stepper motors, can also be used as motor 554. Furthermore, in this embodiment, motion converter 555 is a feed screw mechanism such as a ball screw, but other types of motion converters can also be used.

[0130] The threaded shaft 555a of the motion converter 555 is rotatably supported by a pair of bearings, and one end is connected to the shaft of the motor 554. Additionally, Figure 10 The bearing supporting the threaded shaft 555a is omitted from the diagram. A pair of bearings for the motor 554 and the motion converter 555 are mounted on a rotary table (not shown) that is rotatable about a vertical axis and is provided on the first movable base 522A. The motor 554 is configured such that its shaft intersects perpendicularly with the rotation axis of the rotary table.

[0131] like Figure 10 As shown, the nut 555b (linear motion part) of the motion converter 555 is rotatably connected to the second movable base 522B via a hinge 556 about a vertical axis. When the threaded shaft 555a is rotated by the motor 554, the hinge 556 mounted on the second movable base 522B moves approximately in the Y-axis direction together with the nut 555b. Subsequently, the second movable base 522B rotates about the rotation axis A1, and the test wheel W supported on the second movable base 522B rotates about the contact position P as the fulcrum, causing the tilt angle to change.

[0132] like Figure 8 As shown, motor 554 is connected to control unit 70 via servo amplifier 554a. The phase information of the shaft detected by the rotary encoder RE built into motor 554 is input to control unit 70 via servo amplifier 554a.

[0133] The control unit 70 calculates the current value of the tilt angle based on the signal from the rotary encoder RE built into the motor 554. Based on the tilt angle setting data and the current value input via the interface unit 90, the control unit 70 controls the drive of the motor 554 so that the set tilt angle is applied to the test wheel W.

[0134] The angle of attack applicator 56 is a mechanism that applies an angle of attack to the test wheel W. The angle of attack is the angle formed between the track and the wheel; more specifically, it is the angle formed around the upper and lower axes (i.e., the yaw direction) between the width direction of the track (sleeper direction) and the axial direction of the wheel. In the wheel testing apparatus 1000, the angle of attack is defined as the angle formed around the X-axis between the rotation axis of the track wheel R and the rotation axis of the test wheel W.

[0135] like Figure 10As shown, the support frame 1523 of the wheel support portion 1500 in this embodiment includes: a box-shaped support column 1523a fixed to the third movable base 522C; and an arm 1523b rotatably connected to the support column 1523a about a rotation axis A2 extending in the X-axis direction. Like the arm 523b in the first embodiment, the arm 1523b is a generally L-shaped component when viewed from above, and has: a base portion 1523b1 extending in the Y-axis direction connected to the upper part of the support column 1523a; and a main body 1523b2 extending to the left from the rear end of the base portion 1523b1.

[0136] A rotating support shaft 561 protrudes from the right end of the base 1523b1 in the X-axis direction. Furthermore, a bearing 562, rotatably supporting the rotating support shaft 561, is mounted on the upper part of the support column 1523a. The arm 1523b is rotatably supported by the bearing 562 via the rotating support shaft 561, centered on a rotating shaft A2 extending in the X-axis direction. The bearing 562 is configured with the rotating shaft A2 at a contact position P. That is, the rotating shaft A2 is a straight line perpendicular to the wheel tread of the test wheel W. The rotating support shaft 561 and the bearing 562 constitute part of the angle-of-attack imparting part 56.

[0137] like Figure 9 As shown, the angle-of-attack imparting unit 56 includes: a motor 564; and a motion converter 563 that converts the rotational motion of the motor 564 into linear motion in the Z-axis direction. In this embodiment, the motor 564 is an AC servo motor, but other types of motors with controllable drive quantity (rotation angle), such as a DC servo motor or a stepper motor, can also be used as the motor 564. Furthermore, in this embodiment, the motion converter 563 is a feed screw mechanism such as a ball screw, but other types of motion converters can also be used.

[0138] The threaded shaft of the motion converter 563 is rotatably supported by a pair of bearings, and one end of it is connected to the shaft of the motor 564 via a bevel gear. Alternatively, the threaded shaft of the motion converter 563 can be directly connected to the shaft of the motor 564. The motor 564 and the motion converter 563 are mounted via a hinge having a rotation axis extending in the X-axis direction on a swing frame that is rotatable (i.e., swingable) within a certain angular range around the rotation axis of the hinge.

[0139] The nut (linear motion unit) of the motion converter 563 is pivotally connected to the arm 1523b of the support frame 1523 via a hinge having a rotation axis extending in the X-axis direction, about the rotation axis of the hinge. When the threaded shaft of the motion converter 563 is rotated by the motor 564, the hinge mounted on the arm 1523b moves approximately in the Z-axis direction along with the nut. Subsequently, the test wheel W supported on the arm 1523b rotates and moves together with the arm 1523b about the rotation axis A2 passing through the contact position P (in other words, a straight line perpendicular to the tread surface of the test wheel) to impart an angle of attack.

[0140] like Figure 8 As shown, motor 564 is connected to control unit 70 via servo amplifier 564a. The phase information of the shaft detected by the rotary encoder RE built into motor 564 is input to control unit 70 via servo amplifier 564a.

[0141] The control unit 70 calculates the current value of the angle of attack based on the signal from the rotary encoder RE built into the motor 564. Based on the angle of attack setting data and the current value input via the interface unit 90, the control unit 70 controls the drive of the motor 564 so that the set angle of attack is applied to the test wheel W.

[0142] like Figure 10 As shown, the linear motion section 532a of the motion converter 532 of the wheel weight application section 53 is fixed to the support column 1523a of the support frame 1523 via the wheel weight detector 533. Furthermore, the linear motion section 532a of the motion converter 532 is arranged such that its center line aligns with the rotation axis A2. Therefore, when applying wheel weight, it is possible to prevent the application of large torques to the support frame 1523.

[0143] The embodiments of the present invention have been described above. The embodiments of the present invention are not limited to the descriptions above and can be varied. For example, structures of embodiments illustratively shown in this specification, structures of embodiments that can be clearly understood by those skilled in the art based on the description in this specification, and / or structures obtained by appropriate combinations of known technologies are also included in the embodiments of the present invention.

[0144] The above embodiment is configured such that the wheel weight-applying part 53 is provided on the wheel support part 50, and the wheel weight is adjusted by moving the test wheel W forward and backward relative to the track wheel R. However, the present invention is not limited to this structure. For example, the wheel weight-applying part may also be provided on the track wheel support part, and the wheel weight may be adjusted by moving the track wheel R forward and backward relative to the test wheel W.

[0145] In the above embodiment, the track wheel R is connected to the rotary drive device 10 without passing through the torque generating device 20, and the test wheel W is connected to the rotary drive device 10 via the torque generating device 20. However, the present invention is not limited to this structure. For example, it may be configured such that the track wheel R is connected to the rotary drive device 10 via the torque generating device 20, and the test wheel W is connected to the rotary drive device 10 without passing through the torque generating device 20. Furthermore, it may be configured such that two torque generating devices 20 are provided, with the track wheel R connected to the rotary drive device 10 via one torque generating device 20, and the test wheel W connected to the rotary drive device 10 via the other torque generating device 20.

[0146] In the above embodiment, a structure is adopted in which multiple three-component force sensors are provided in the wheel support 50, and the measuring unit 80 measures the torque and wheel weight applied to the test wheel W based on the detection results of the multiple three-component force sensors. However, the present invention is not limited to this structure. For example, it can also be configured to measure torque and wheel weight based on the detection results of multiple two-component force sensors or one-component force sensor.

[0147] In the above embodiments, the power distribution mechanism is incorporated into the track wheel support portion 32, but it can also be configured to be separate from the track wheel support portion 32. For example, the first transmission portion 30 can be disconnected from the track wheel support portion 32, and the rotary drive device 10 and the first transmission portion 30 can be connected via an additional power transmission mechanism (e.g., a winding drive or gear drive). In this case, the drive pulley 311 of the first belt mechanism portion 31 and the shaft of the rotary drive device 10, which is equipped with the pulley and gear of the additional power transmission mechanism, function as a power distribution mechanism.

[0148] In the second embodiment described above, the fixed base 51 and the spindle 527 are connected sequentially via the transverse pressure imparting part 54, the tilt angle imparting part 55, the wheel weight imparting part 53 and the angle of attack imparting part 56. However, the present invention is not limited to this structure, and the transverse pressure imparting part 54, the tilt angle imparting part 55, the wheel weight imparting part 53 and the angle of attack imparting part 56 can be connected in any order.

Claims

1. A wheel testing device, characterized in that, include: A track wheel support that rotatably supports the track wheel; The wheel support supports the test wheel in a rotatable manner while in contact with the track wheel; A first electric motor that rotates the track wheel and the test wheel; A power distribution mechanism that distributes the power generated by the first electric motor to the track wheel and the test wheel; and A torque generating device that produces the torque imparted to the test wheel. The torque generating device includes: A rotating frame driven by the rotation of the first electric motor; and The second motor is installed on the rotating frame. At least one of the track wheel and the test wheel is connected to the first electric motor via the torque generating device. When the second motor stops operating, the track wheel and the test wheel rotate in opposite directions at approximately the same circumferential speed. The rated power of the second motor is 3kW or more, and the moment of inertia of the rotating part of the second motor is 0.01 kg·m. 2 the following.

2. The wheel testing device as described in claim 1, characterized in that: The torque generating device has an output shaft coaxially configured with the rotating frame.

3. The wheel testing device as described in claim 2, characterized in that: The torque generating device has a bearing unit that rotatably supports the rotating frame. The rotating frame has a cylindrical shaft portion supported by the bearing unit. A bearing is provided on the inner circumference of the shaft. The output shaft is rotatably supported by the bearing through the hollow portion of the shaft.

4. The wheel testing device as described in claim 1, characterized in that: The second motor is coaxially configured with the rotating frame.

5. The wheel testing device as described in claim 1, characterized in that: The second motor is fixed to the rotating frame via a plurality of rod-shaped connecting parts arranged radially around the rotation axis of the rotating frame.

6. The wheel testing device as described in claim 1, characterized in that: The rotating frame has a cylindrical motor housing for housing the second electric motor.

7. The wheel testing apparatus as described in any one of claims 1 to 6, characterized in that, include: A control unit that controls the first motor and the second motor; A speed measuring mechanism for measuring the rotational speed of the track wheel; and A torque measuring mechanism for measuring the torque of the test wheel. The control unit controls the drive of the first motor based on the measurement results of the speed measuring mechanism, and controls the drive of the second motor based on the measurement results of the torque measuring mechanism.

8. The wheel testing device as described in claim 1, characterized in that: It includes a wheel weight-assigning unit that assigns wheel weight to the test wheel by moving one of the test wheel and the track wheel forward or backward relative to the other.

9. The wheel testing device as described in claim 1, characterized in that: It includes an angle-of-attack imparting unit, which imparts an angle of attack by rotating one of the test wheel and the track wheel relative to the other about a straight line perpendicular to the tread surface of the test wheel.

10. The wheel testing device as described in claim 1, characterized in that: It includes an angle-granting section, which imparts an angle by rotating one of the test wheel and the track wheel about a tangential line relative to the other.

11. The wheel testing device as described in claim 1, characterized in that: It includes a lateral pressure application section, which applies lateral pressure to the test wheel by moving one of the test wheel and the track wheel axially relative to the other.

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