JP2007093212A - Test run arrangement - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a belt type test run arrangement for a vehicle which executes various tests of an automobile by rotating wheels of the automobile and the like, maintaining static state of the frame of the vehicle and can prevent the gap of an endless belt. <P>SOLUTION: The above problem is resolved by constituting the endless belt with a support member supporting the endless belt touching both ends of the width direction. Desirably, a plurality of guide rollers of which the support member rotates together with the rotation of the endless belt is provided. More desirably, the shafts of the guide rollers are attached to a plurality of spring means for energizing each of the guide rollers toward the endless belt. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a vehicular running test apparatus that performs various tests of an automobile by rotating a wheel while a frame of a vehicle such as an automobile is stationary.

  In recent years, instead of running a car on a test course, a running test apparatus that performs various measurements by moving a car indoors is being used. In a running test apparatus, a drum or an endless belt is brought into contact with a driving wheel of an automobile so that the body of the automobile does not move even when the driving wheel rotates. Such a traveling test apparatus performs various tests such as measurement of vehicle body vibration and in-vehicle noise during traveling, measurement of exhaust gas, and test of effectiveness of the steering wheel.

In such a running test apparatus, a belt type that abuts the tire on a flat surface is more suitable than a drum type that abuts the tire on a curved surface. As such a belt-type running test apparatus, there is one described in Patent Document 1.
JP-A-6-207886

  In the case of such a belt-type running test apparatus, if a deviation occurs in the circumferential direction of the tire and the traveling direction of the endless belt, a lateral force is applied to the belt. When the lateral force exceeds a predetermined value, the endless belt is displaced laterally from the roller pair. Since this belt displacement may cause the endless belt to drop or break, it is desirable to avoid it as much as possible.

  In the configuration of Patent Document 1, the rotation shaft of the roller pair on which the endless belt is engaged can be tilted, and when a shift of the endless belt is detected, the endless belt moves in a direction opposite to the shift. In this way, the rotation axis of the roller pair is tilted to correct the deviation.

  When investigating the behavior of a tire when the vehicle is traveling straight by a running test device, it is desirable to prevent the endless belt from shifting as much as possible. On the other hand, the configuration of Patent Document 1 is to prevent the progress of the shift and correct the shift, and does not prevent the shift. For this reason, a running test apparatus capable of preventing the endless belt from shifting has been desired.

  In order to achieve the above object, the running test apparatus of the present invention has a support member that contacts the both ends in the width direction of the endless belt and supports the endless belt. With such a configuration, the endless belt can be prevented from shifting by the support member. As this support member, for example, a plurality of guide rollers that rotate as the endless belt rotates can be considered. When supporting a belt that travels at a high peripheral speed of 100 to 200 km / h, a support member that rotates as the belt travels, such as a guide roller, is used to prevent and support the wear of the support member. The life of the member can be extended.

  The shafts of the plurality of guide rollers may be attached to a plurality of spring means that urge each of the plurality of guide rollers toward the endless belt. With such a configuration, the guide rollers are not separated from the endless bells, and each guide roller receives a force from the endless belt almost evenly. Therefore, the load can be generated when the load is concentrated on a specific guide roller. Abrupt progress of wear of the guide roller is prevented. As a result, the life of the guide roller can be further extended.

  Furthermore, by coating the circumferential surface of the guide roller and both ends in the width direction of the endless belt, the surface roughness of the circumferential surface of the guide roller and both ends in the width direction of the endless belt is reduced, and the force applied to the guide roller is reduced. It becomes possible to reduce. Thereby, the wear of the guide roller is reduced, and the life of the guide roller can be further extended.

  As described above, according to the present invention, a traveling test apparatus capable of preventing the endless belt from shifting is realized.

  Hereinafter, a traveling test apparatus according to an embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a side view of a chassis dynamometer 1 as a running test apparatus according to an embodiment of the present invention. FIG. 2 is a top view of the chassis dynamometer 1. The chassis dynamometer 1 is a device that gives various running measurements to the driving wheels (front wheels in the present embodiment) of the vehicle in the same running state as when the vehicle is actually running. The measurement result is transmitted to the control unit 800 (described later) of the chassis dynamometer 1, and the measurement result is processed by the control unit 800.

  As shown in FIG. 1, the chassis dynamometer 1 includes a pair 100 on which a frame 100 for fixing the body of the automobile C to be tested and a front wheel Wf of the automobile C are respectively mounted. Flat belt mechanisms 200 and 300 (see FIG. 2), and a slope 400 for moving the automobile C onto the gantry 100 and the flat belt mechanism 200. In the present embodiment, the automobile C is front wheel drive. In the following description, the front side of the car C is defined as “front”, the rear side of the car C is defined as “rear”, and the width direction of the car C is defined as “width direction”.

  As shown in FIG. 1, an L-shaped guide 110 for fixing the body Cb of the automobile C and a pair of tires for fixing two wheels of the rear wheel Wb of the automobile C on the gantry 100, respectively. Grasping means 120 and 130 are provided.

  Three L-shaped guides 110 are provided on each of the left and right sides of the automobile C so that one end 111 thereof is in contact with both side surfaces of the body Cb of the automobile C. A pad 112 (FIG. 2) made of rubber, urethane, or the like is provided at one end 111 of each L-shaped guide 110 that comes into contact with the body Cb of the automobile C, and friction acting between the pad 112 and the body Cb. The vehicle C is held so as not to move by force. Further, each L-shaped guide 110 can adjust the position in the left-right direction and the height of one end 111 of the L-shaped guide 110 in order to correspond to automobiles of various widths and shapes. Various known position adjustment mechanisms such as a rack-pinion mechanism, a feed screw mechanism, and a hydraulic mechanism can be used as a mechanism for performing this adjustment.

  In this embodiment, the L-shaped guide 110 holds the vehicle C by sandwiching the body Cb of the vehicle C from both ends in the width direction. However, the present invention is not limited to the above configuration, and the jack of the vehicle is used. A mechanism for fixing the up point to the gantry 100 may be used instead.

  The tire gripping means 120 (130) has clamps 122 (132) and 124 (134) for gripping the tire from the front and rear. The clamps 122 (132) and 124 (134) are respectively movable in the front-rear direction, and grip and fix the tire of the automobile C from the front and rear. As the clamp moving mechanism, various known position adjusting mechanisms such as a rack-pinion mechanism, a feed screw mechanism, and a hydraulic mechanism can be used.

  As described above, in the present embodiment, since the vehicle C is front-wheel drive, the front wheel Wf is placed on the flat belt mechanisms 200 and 300, and the rear wheel Wb is fixed on the gantry 100. When the automobile C is rear wheel drive, the rear wheel Wb is placed on the flat belt mechanisms 200 and 300 and the front wheel Wf is fixed on the gantry 100. Furthermore, when the automobile C is a four-wheel drive, four flat belt mechanisms are prepared so that all the drive wheels are mounted on separate flat belts.

  When the automobile C is installed in the chassis dynamometer 1 configured as described above and the front wheels Wf of the automobile C are driven, the endless belts of the flat belt mechanisms 200 and 300 rotate with the rotation of the front wheels Wf. At this time, various running states can be reproduced by applying resistance to the endless belt by a drive absorption motor provided in the flat belt mechanisms 200 and 300. For example, a downhill can be reproduced by applying resistance in the same direction as the traveling direction of the endless belt, and an uphill can be reproduced by applying resistance in the direction opposite to the traveling direction of the endless belt. Further, by measuring the peripheral speed of the flat belt using a rotary encoder, which will be described later, and applying a load corresponding to the acceleration of the flat belt, the inertial force during acceleration / deceleration can be applied to the vehicle body of the automobile. That is, it is possible to reproduce a transient running state during acceleration / deceleration of the automobile.

  The structure of the flat belt mechanism 200, 300 will be described below. FIG. 3 is a side view of the flat belt mechanism 200 according to the present embodiment. FIG. 4 is a top view of the flat belt mechanism 200. As shown in FIG. 4, the flat belt mechanism 300 is configured and arranged symmetrically with the flat belt mechanism 200, and the structure is the same as the flat belt mechanism 200. The description about this is omitted.

  As shown in FIG. 3, the flat belt mechanism 200 includes a driving roller 212 extending in the width direction, a roller pair 210 including a driven roller 214, and an endless belt 220 stretched over the roller pair 210. Have. The driving roller 212 and the driven roller 214 are arranged side by side in the front-rear direction. As the driving roller 212 rotates, the endless belt 220 rotates around the roller pair 210, and as the endless belt 220 moves, The driven roller 214 rotates. The diameters of the driving roller 212 and the driven roller 214 are about 560 mm.

  The endless belt 220 is a steel plate having a thickness of about 0.5 mm, and a rubber anti-slip material 222 such as Safety Walk (registered trademark) is attached to the outer peripheral surface thereof. This anti-slip material has a higher friction coefficient than the steel endless belt 220 itself, and a state close to an actual asphalt road surface is reproduced.

  The rotation shafts 212a and 214a of the driving roller 212 and the driven roller 214 are rotatably supported by bearings 232 and 234, respectively. The bearings 232 and 234 are provided at both ends of the rotation shafts 212a and 214a of the driving roller 212 and the driven roller 214, respectively.

  The bearing 234 that supports the rotating shaft 214a of the driven roller 214 is provided with a driven roller adjusting mechanism 216 for moving the shaft 224 in the front-rear direction by a feed screw mechanism. By operating the driven roller adjustment mechanism 216, the driven roller 214 can be moved and the distance between the driven roller 214 and the driving roller 212 can be adjusted. As shown in FIG. 4, the driven roller adjusting mechanism 216 is provided at both ends of the driven roller 214.

  Thereby, the tension of the endless belt 220 is adjusted to an appropriate value. The driven roller adjustment mechanism 216 is also used when the endless belt 220 is replaced. That is, when the endless belt 220 is attached to or detached from the roller pair 210, the driven roller 214 is moved in a direction to reduce the distance between the driven roller 214 and the driving roller 212, so that the endless belt 220 is moved without applying force. The belt 220 is detachable.

  Both the bearing 232 and the driven roller adjusting mechanism 216 provided on the driving roller 212 are fixed to the roller support guides 236 and 237. Since a pair of bearings 232 and 234 are provided at both ends in the width direction of the roller pair 210, one roller support guide 236 and 237 is also provided at each of the both ends in the width direction of the roller pair 210 (FIG. 4). reference). The roller support guide 236 on the front side in FIG. 3 includes a plate portion 236a extending on a surface substantially perpendicular to the rotation shafts 212a and 214a of the drive roller 212 and the driven roller 214, and outward in the width direction from both front and rear ends of the plate portion 236a. A front wall surface 236b and a rear wall surface 236c are formed to extend toward the front. The bearing 232 is fixed to the rear wall surface 236c. The driven roller adjusting mechanism 216 is fixed to the front wall surface 236b. In order to improve the rigidity of the roller support guide 236, the lower ends of the front wall surface 236b and the rear wall surface 236c are connected to each other via a lower wall surface 236d extending in the front-rear direction. The roller support guide 237 has a similar configuration.

  The roller support guides 236 and 237 are both fixed on the main support plate 238. That is, the bearings 232 and 234 are fixed to the single main support plate 238 via the roller support guides 236 and 237. Therefore, the load and vibration applied to the endless belt 200 from the front wheel Wf of the automobile C are transmitted to the main support plate 238.

  As shown in FIG. 3, the main support plate 238 is fixed on the base plate 700 with bolts 710. Further, quartz piezoelectric three-component force sensors 721 to 724 are provided between the main support plate 238 and the base plate 700 (only 721 and 722 are shown in FIG. 3). The load sensors 721 to 724 are disposed at the four corners of the roller support plate 236, respectively. Reference numerals 721 to 724 each have a perforated disk shape. A bolt 710 is inserted into the hole, and the bolt 710 fastens the load sensors 721 to 724 to the roller support plate 236 and the base plate 700, whereby predetermined loads are applied to the load sensors 721 to 724. Preload is added.

  A drive motor 242 for applying a load to the endless belt 220 is provided between the drive roller 212 and the driven roller 214. The drive motor 242 is fixed at both ends in the width direction to the roller support guides 236 and 237 in the form of a fixed beam. As a result, the drive motor 242 is supported in a floating state and does not contact the endless belt 220. The rotation shaft 242a of the drive motor 242 passes through an opening 236e provided at the center of the plate portion 236a of the roller support guide 236 and protrudes outward from the roller support guide 236. A pulley 244 is fixed to the tip of the rotation shaft 242a of the drive motor 242. The pulley 244 and the pulley 212b fixed to the tip of the rotation shaft 212a of the drive roller 212 are connected via an endless belt 243. Therefore, the power applied to the rotating shaft 242a of the drive motor 242 is transmitted to the endless belt 220 via the pulley 244, the endless belt 243, the pulley 212b, and the drive roller 212. That is, a load can be applied to the endless belt 220 by the drive motor 242.

  In order to support the rotating shaft 242a at a position closer to the tip of the rotating shaft 242a of the driving motor 242, that is, a position close to the pulley 244, the driving motor bearing 245 includes a front wall surface 236b and a rear wall surface 236c of the roller support guide 236. Is fixed on a bearing fixing plate 239 that is passed to the end face on the outer side in the width direction. An opening 239a for allowing the rotation shaft 242a of the drive motor 242 to pass is formed in the center of the bearing fixing plate 239.

  As described above, in the chassis dynamometer 1 of the present embodiment, the drive motor 242 for absorbing drive and the various members (pulleys 244 and the like) associated with the drive motor 242 all have the roller support guides 236 and 237. Via the main support plate 238. For this reason, both the mechanical loss transmitted from the rotating shaft 242a of the drive motor 242 to the drive roller 212 and the reaction force of the mechanical loss transmitted to the drive motor 242 itself are applied to the load sensor. Only the load transmitted from the front wheel Wf of the automobile to the endless belt 220 is detected by the load sensors 721 to 724 almost accurately. That is, in the chassis dynamometer 1 of the present embodiment, it is possible to accurately detect the load fluctuation and vibration transmitted from the front wheel Wf.

  A rotary encoder 217 (described later) (not shown) is provided on the rotation shaft 214 a of the driven roller 214. The rotational speed of the driving roller 212 is measured by the rotary encoder 217, and the speed of the endless belt 220, that is, the peripheral speed of the front wheel Wf in contact with the endless belt 220 is measured from the measurement result. A rotary encoder (not shown) is also provided on the rotation shaft 212 a of the drive roller 212. When there is a difference between the rotational speed detected by the encoder on the driving roller 212 side and the rotational speed detected by the encoder 217 on the driven roller 213 side, slip occurs between the driving roller 212 and the endless belt 220. Means that The control unit 800 determines whether or not slippage has occurred between the drive roller 212 and the endless belt 220 from the rotational speeds detected by the rotary encoder 217 and the rotary encoder on the drive roller 214 side. If it is determined, the operator is notified of the abnormality of the apparatus.

  The support roller mechanism 600 for supporting the upper part of the endless belt 220 will be described below. As shown in FIG. 3, the support roller mechanism 600 includes five rollers 611 to 615 that are arranged in the front-rear direction and whose rotation axes are in the left-right direction. Both ends of the rollers 611 to 615 are rotatably supported by bearings 622 and 624 provided on the roller support guides 236 and 237. The heights of the upper ends of the rollers 611 to 615 are adjusted to be the same as or slightly higher than the heights of the upper ends of the driving roller 212 and the driven roller 214. For this reason, the upper ends of the rollers 611 to 615 are always in close contact with the inner peripheral upper portion of the endless belt 220. Therefore, in a state where the front wheel Wf is placed on the flat belt mechanism 200, the front wheel Wf is supported not only by the endless belt 220 but also by the rollers 611 to 615.

  As described above, the chassis dynamometer 1 of the present embodiment places the driving wheels of the automobile C on the flat belt mechanism, and then drives the driving wheels to advance and retract the endless belt of the flat belt mechanism. Here, when the rotation shaft of the driving wheel is inclined with respect to the rotation shaft of the roller of the flat belt mechanism, that is, when there is a deviation between the traveling direction of the automobile and the traveling direction of the endless belt, a lateral force is applied to the endless belt. In the present embodiment, a guide roller mechanism for preventing the endless belt from moving in the width direction that can be generated by the lateral force is provided.

  The guide roller mechanism 250 provided in the flat belt mechanism 200 will be described below. The flat belt mechanism 300 is also provided with a similar guide roller mechanism. The guide roller mechanism 250 includes a disk-shaped guide roller 251 that contacts both ends of the lower end of the endless belt 220 in the width direction, and a bearing plate 252 that rotatably supports the guide roller 251. In the present embodiment, two sets of guide roller mechanisms 250 are provided at one end in the width direction of the endless belt 220 and two sets at the other end, and are supported from both ends of the endless belt 220. In this embodiment, the guide roller mechanism 250 is configured to support both ends of the lower end of the endless belt 220 in the width direction, but the guide roller mechanism 250 supports both ends of the upper end of the endless belt 220 in the width direction. Alternatively, the guide roller mechanism 250 may support both ends in the width direction of the endless belt 220 at both the upper and lower portions of the endless belt 220.

  The bearing plate 252 of the guide roller mechanism 250 is fixed on the main support plate 238. As shown in FIG. 4, long holes 252a extending in the width direction are formed at both ends of the bearing plate 252 in the front-rear direction, and bolts (not shown) are formed through the long holes 252a. The bearing plate 252 is fastened to the main support plate 238. In the present embodiment, since the bearing plate 252 is fixed through a pair of elongated holes, the position of the bearing plate 252 with respect to the main support plate 238 can be adjusted in the width direction. As shown in FIG. 3, most of the guide roller mechanism 250 is located on the outer side in the width direction with respect to the plate portion 236 a of the roller support guide 236. In this state, a notch 236f is provided in the lower portion of the plate portion 236a so that the guide roller 251 can pass through the plate portion 236a and contact the endless belt 220.

  An enlarged view of the guide roller mechanism 250 is shown in FIG. As illustrated, a groove 251 a extending in the circumferential direction is formed on the cylindrical surface of the guide roller 251. The width of the groove 251a is slightly larger than the thickness of the endless belt 220. In the state where the guide roller mechanism 250 is attached to the flat belt mechanism 200, the end portion in the width direction of the endless belt 220 enters the groove 251a.

  The bearing plate 252 is fitted with a bearing portion 252b for supporting the rotation shaft 251b of the guide roller 251. The bearing portion 252b is urged toward the endless belt 220 by a spring (not shown) built in the bearing plate 252. As a result, the groove 251a of the guide roller 251 contacts the endless belt 220. Further, since the groove 251a and the endless belt 220 are always in contact with each other, the endless belt 220 is guided by the groove 251a and does not move in the vertical direction.

  Further, the guide rollers 251 of the four sets of guide roller mechanisms 250 are urged toward the endless belt 220, and each of the guide rollers 251 comes into contact with the endless belt 220 with a substantially equal load. . As a result, slip is unlikely to occur between the endless belt 220 and the guide roller 251. When a slip occurs between the endless belt 220 and the guide roller 251, the wear of the guide roller 251 proceeds. Therefore, the life of the guide roller 251 can be extended by the configuration of the present embodiment.

  In order to further prevent the guide roller 251 from being worn, the guide roller 251 is formed of a material having high hardness such as iron that has been quenched. Furthermore, the end faces of the endless belt 220 in the width direction and the cylindrical surface of the guide roller 251 are coated with hard chrome plating or the like. For this reason, the end surfaces of the endless belt 220 at both ends in the width direction and the cylindrical surface of the guide roller 251 are smoothly formed, and the contact area between the two is reduced. As a result, the load in the front-rear direction applied from the endless belt 220 to the guide roller 251 is reduced, and the guide roller 251 is less likely to be worn.

  The processing of the output of the load sensors 721 to 724 and the rotary encoder 217 and the control of the drive motor 242 (and the processing of the output of the sensor on the side of the flat belt mechanism 300 corresponding to these and the control of the motor) are performed by the control unit 800. Done. FIG. 6 shows a block diagram of the control unit 800.

  Each of the load sensors 721 to 724 is connected to the charge amplifiers 821 to 824, whereby the outputs of the load sensors 721 to 724 are amplified. Outputs of the charge amplifiers 821 to 824 are input to signal input terminals 831a to 834a of the filter amplifiers 831 to 834.

  Each of the filter amplifiers 831 to 834 removes noise from the input signal and amplifies the signal level at a predetermined amplification factor. Each of the filter amplifiers 831 to 834 has control signal output terminals 831b to 834b and 831c to 834c, which are connected to the controller 801. The filter amplifiers 831 to 834 amplify the input signal at any one of two preset amplification factors A1 and A2. The signals amplified at the amplification factor A1 are discretized by the A / D converters 841a to 844a via the signal output terminals 831b to 834b of the amplifiers 831 to 834. The signal amplified at the amplification factor A2 is discretized by the A / D converters 841b to 844b via the signal output terminals 831c to 834c of the amplifiers 831 to 834. A2 has a higher amplification factor than A1.

  The discretized signal is input to the controller 801 and processed. In the present embodiment, for simplification, the output from each of the load sensors 721 to 724 is shown as being configured to be processed by one signal processing system, but each of the load sensors 721 to 724 is 3 minutes. Since it is a force load sensor, it has three output terminals each. Accordingly, each processing system has a 3-channel signal processing system. The controller 801 calculates the orthogonal three-axis direction component of the force transmitted from the front wheel Wf of the automobile C to the endless belt 220 by adding the outputs of the load sensors 721 to 724 for each axis. Further, by calculating the outputs of the load sensors 721 to 724 using a known predetermined method, the controller 801 calculates moments about three orthogonal axes transmitted from the front wheels Wf of the automobile C to the endless belt 220.

  The output pulse of the rotary encoder 217 is input to the controller 801 as it is. The controller 801 is connected to a timer 802 that measures time, and by measuring the pulse interval output from the rotary encoder 217 with reference to the timer 802, the rotational speed of the rotary encoder 217 (that is, the driven roller 214). Measure.

  Further, the control unit 800 has an external input terminal 803, and various sensors (exhaust gas concentration detection sensor, flow rate sensor, etc. of the automobile C) provided outside the apparatus can be connected. The sensor output input from the external input terminal 803 is input to the controller 801.

  The controller 801 is connected to the drive motor 242 and controls the operation of these drive motors.

  The controller 801 is connected to a monitor 861 for displaying an index obtained by processing the output from each sensor, and a keyboard 862 for inputting various data to the control unit 800. The operator of the running test apparatus 1 can perform various controls of the chassis dynamometer 1 such as adjusting the torque of the drive motor 242 and recording measurement results by inputting various data from the keyboard 862.

  The control unit 800 described above describes the relationship between the sensor and motor on the flat belt mechanism 200 side, but the sensor and motor on the flat belt mechanism 300 side are similarly connected to the control unit 800. It is possible to process signals from sensors and to control motors.

It is a side view of the chassis dynamometer of the embodiment of the present invention. It is a top view of the chassis dynamometer of the embodiment of the present invention. It is a side view of the flat belt mechanism of the embodiment of the present invention. It is a top view of the flat belt mechanism of the embodiment of the present invention. It is an enlarged view of the guide roller mechanism of the embodiment of the present invention. It is a block diagram of the control part of the chassis dynamometer of the embodiment of the present invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Chassis dynamometer 100 Base 110 L-shaped guide 120, 130 Tire grip means 122, 124 Clamp 132, 134 Clamp 200, 300 Flat belt mechanism 210 Roller pair 212 Drive roller 212a Rotating shaft 212b Pulley 214 Followed roller 216 Followed roller adjustment mechanism 217 Rotary encoder 220 Endless belt 222 Anti-slip material 232, 234 Bearing 236, 237 Roller support guide 238 Main support plate 242 Drive motor 244 Pulley 245 Bearing 250 Guide roller mechanism 251 Guide roller 251a Groove 251b Rotating shaft 252 Bearing plate 252a Long hole 400 Slope 500 Support belt mechanism 510, 520 Roller 512, 522 Bearing 523 Roller adjustment mechanism 530 Endless belt 540 Shaft Support member 600 Support roller mechanism 611 to 615 Support roller 700 Base plate 710 Bolt 721 to 724 6 Component force sensor 800 Control unit 801 Controller 803 External input terminal 821 to 824 Charge amplifier 831 to 834 Filter amplifier 841 to 844 A / D converter 861 Monitor 862 Keyboard C Car Cb Car body Wf Front wheel Wb Rear wheel

Claims (10)

With Laura pair,
A bearing portion having a pair of bearings for rotatably supporting each of the roller pairs;
An endless belt stretched over the roller pair;
Have
At least one of tires mounted on a vehicle is in contact with the endless belt, and the endless belt rotates around the pair of rollers as the at least one tire rotates. ,
The travel test apparatus further comprising a support member that contacts the both ends in the width direction of the endless belt and supports the endless belt.   The travel test apparatus according to claim 1, wherein the support member is a plurality of guide rollers that rotate as the endless belt rotates.   3. The travel test apparatus according to claim 2, wherein the shafts of the plurality of guide rollers are attached to a plurality of spring means that urge each of the plurality of guide rollers toward the endless belt. . A groove extending in the circumferential direction is formed on the cylindrical surface of the guide roller,
The widthwise end of the endless belt enters the groove;
The running test apparatus according to claim 2 or 3, wherein   5. The travel test apparatus according to claim 2, wherein a circumferential surface of the guide roller and both ends in the width direction of the endless belt are coated.   The traveling test apparatus according to claim 5, wherein the coating is hard chrome plating.   The travel test apparatus according to claim 2, wherein the guide roller is formed of iron that has been quenched. A bearing support member to which a housing of a pair of bearings of the bearing portion is fixed;
A base for supporting the bearing support member from below;
A load sensor disposed between the bearing support member and the base for measuring a force transmitted from a vehicle tire to the flat belt mechanism;
The travel test apparatus according to claim 1, further comprising: A plurality of support rollers;
The support roller contacts the endless belt;
The endless belt is sandwiched between at least one of the plurality of support rollers and the at least one tire;
The travel test apparatus according to claim 1, wherein   The travel test apparatus according to any one of claims 1 to 9, further comprising a drive absorption motor disposed between rollers constituting the roller pair.

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