JP7240021B2 - tire test equipment - Google Patents

Description

The present invention relates to tire testing equipment.

By adopting an ultra-low inertia servomotor whose inertia is greatly reduced compared to conventional servomotors, the present inventors have developed a servomotor capable of repeatedly applying a high frequency load of several tens to several hundred Hz. Various types of fatigue test equipment and vibration test equipment have been put into practical use (for example, Patent Document 1).

The servo-motor type test rig described above has many of the serious problems that conventional hydraulic test rigs have had (e.g., the need to install large-scale hydraulic supply equipment such as oil tanks and hydraulic piping, and the The range of application is rapidly expanding because it solves the problem of working environment and soil contamination caused by leakage of hydraulic oil, which requires replacement of hydraulic oil.

WO2008/133187

SUMMARY OF THE INVENTION An object of the present invention is to provide a tire testing apparatus capable of testing tires simulating actual driving conditions.

According to one aspect of the present invention, a mechanism that rotatably supports a wheel on which a tire, which is a test piece, is mounted and presses a tread portion of the tire against a simulated road surface, a torque applying unit that applies torque to the wheel, a first electric motor for rotationally driving a torque imparting unit, the torque imparting unit being rotated by a casing driven by the first electric motor; a second electric motor attached to the casing; and a connecting shaft to be driven, wherein the second electric motor has a rated output of 10 kW or more and a moment of inertia of the rotating part of 10 ⁻² kg·m ² or less.

In the above tire testing apparatus, a mechanism for rotatably supporting a wheel on which a tire as a test piece is mounted and pressing the tread portion of the tire against a simulated road surface, a torque applying unit for applying torque to the wheel, and a torque applying a first electric motor for rotationally driving the unit, the torque imparting unit comprising a casing rotationally driven by the first electric motor; a second electric motor mounted on the casing; The shaft may be arranged concentrically with the rotation axis of the casing.

In the tire testing apparatus described above, the torque applying unit may have a connecting shaft that is rotationally driven by the second electric motor.
In the above tire testing apparatus, the torque applying unit includes a bearing for rotatably supporting the casing, the casing has a cylindrical shaft rotatably supported by the bearing, and the inner circumference of the shaft is Furthermore, a bearing may be provided to rotatably support the connecting shaft passed through the hollow portion of the shaft portion.

According to another aspect of the present invention, a mechanism for rotatably supporting a wheel mounted with a tire, which is a test piece, and pressing the tread portion of the tire against a simulated road surface, and a torque applying unit for applying torque to the wheel. and a first electric motor for rotationally driving a torque applying unit, wherein the torque applying unit is attached to a casing rotatably driven by the first electric motor, a bearing for rotatably supporting the casing, and the casing. a second electric motor; and a connecting shaft that is rotationally driven by the second electric motor, the connecting shaft being arranged concentrically with the rotating shaft of the casing, the casing having a cylindrical shaft portion, and the shaft portion In the above, there is provided a tire testing device which is rotatably supported by a bearing portion and provided with a bearing on the inner circumference of the shaft portion for rotatably supporting a connecting shaft passed through a hollow portion of the shaft portion.

The above tire testing apparatus may include a torque sensor for detecting the torque of the connecting shaft, and the torque sensor may include a strain gauge attached to a portion of the connecting shaft accommodated within the shaft portion.

According to yet another aspect of the present invention, a mechanism for rotatably supporting a wheel on which a tire, which is a specimen, is mounted, and pressing the tread portion of the tire against a simulated road surface, and a torque applying unit for applying torque to the wheel a first electric motor for rotationally driving a torque imparting unit, the torque imparting unit being rotationally driven by the first electric motor; a second electric motor attached to the casing; a cylindrical shaft rotatably supported by the bearing, and a torque sensor for detecting the torque of the connecting shaft. A bearing that rotatably supports the connecting shaft passed through the hollow portion of the shaft is provided on the inner periphery of the shaft, and a torque sensor is attached to a portion of the connecting shaft accommodated in the shaft. A tire testing apparatus is provided with an attached strain gauge.

In the tire testing apparatus described above, a constricted portion may be formed in the portion of the connecting shaft that is accommodated in the shaft portion, and a strain gauge may be attached to the constricted portion.
The tire testing apparatus described above includes a control unit that controls the first electric motor and the second electric motor, and a rotation speed measurement unit that measures the rotation speed of the torque applying unit, wherein the control unit controls the rotation speed measurement unit. A configuration may be adopted in which the driving of the first electric motor is controlled based on the measurement result, and the driving of the second electric motor is controlled based on the detection result of the torque sensor.

In the tire testing apparatus described above, the casing may be cylindrical, and the second electric motor may be arranged in the hollow portion of the casing.
In the tire testing apparatus described above, the shaft of the second electric motor may be arranged concentrically with the rotating shaft of the casing.
In the tire testing apparatus described above, the second electric motor may include a motor case, and the motor case may be fixed to the casing via a plurality of fixing rods.
In the above tire testing apparatus, the motor case may include a bracket provided with a second bearing that rotatably supports the shaft of the second electric motor, and one end of the fixed rod may be fixed to the bracket. .
In the tire testing apparatus described above, the casing may have a tubular body portion that houses the second electric motor, and the other end of the fixed rod may be fixed to the body portion.
In the tire testing apparatus described above, the torque applying unit includes a reduction gear that reduces the rotation of the second electric motor, the reduction gear includes a mounting flange, and the mounting flange is sandwiched between the body and the shaft and tightened. Therefore, it may be fixed to the casing.
In the tire testing apparatus described above, a belt mechanism for transmitting the power of the first electric motor to the torque applying unit may be provided, and the casing may have a pulley portion around the outer periphery of which the belt of the belt mechanism is wound.

In the tire testing apparatus described above, a power supply unit arranged outside the casing for supplying power to the second electric motor, a power transmission line for transmitting power from the power supply unit to the second electric motor,
wherein the power transmission line comprises an external power transmission line arranged outside the casing, an internal power transmission line arranged inside the casing and rotatable together with the casing, and an external power transmission line and an internal power transmission line It is good also as a structure provided with the slip ring part to connect.

The tire testing apparatus described above may be configured to include an alignment control mechanism capable of adjusting the alignment of the wheels.
In the above-described tire testing apparatus, the alignment control mechanism may include a tire load adjusting section that adjusts the tire load by moving the position of the rotation axis of the wheel in a direction perpendicular to the simulated road surface.
In the tire testing apparatus described above, the alignment control mechanism may include a slip angle adjustment section that can adjust the slip angle of the tire with respect to the simulated road surface by tilting the rotation axis of the wheel about the normal to the simulated road surface.
In the tire testing apparatus described above, the alignment control mechanism may include a camber angle adjustment section that can adjust the camber angle by tilting the rotation axis of the wheel with respect to the simulated road surface.
The above tire testing apparatus may be configured to include a traverse device for moving the wheel in the direction of its rotation axis.

According to the configuration of one embodiment of the present invention, it is possible to test tires simulating actual driving conditions.

1 is a side view of a biaxial output servomotor according to an embodiment of the present invention; FIG. It is a side view of the servo motor unit which concerns on embodiment of this invention. FIG. 5 is a vertical cross-sectional view of a modification of the servo motor unit according to the embodiment of the present invention; BRIEF DESCRIPTION OF THE DRAWINGS It is a side view of the rotational torsion testing apparatus which concerns on 1st Embodiment of this invention. FIG. 2 is a vertical cross-sectional view of the vicinity of a load applying section of the rotational torsion testing device according to the first embodiment of the present invention; BRIEF DESCRIPTION OF THE DRAWINGS It is a block diagram which shows schematic structure of the control system of the rotation torsion test apparatus which concerns on 1st Embodiment of this invention. FIG. 5 is an external view of a power simulator according to a modification of the first embodiment of the present invention; FIG. 5 is an external view of a power simulator according to a modification of the first embodiment of the present invention; It is a side view of a test device provided with a power simulator according to a modification of the first embodiment of the present invention. FIG. 4 is a partially enlarged view of a test device provided with a power simulator according to a modified example of the first embodiment of the present invention; It is a top view of the rotation torsion test equipment concerning a 2nd embodiment of the present invention. It is a side view of the rotation torsion test equipment concerning a 2nd embodiment of the present invention. It is a longitudinal cross-sectional view of the vicinity of the load applying section of the rotational torsion test device according to the second embodiment of the present invention. It is a top view and a side view of a torsion testing device according to a third embodiment of the present invention. It is a sectional side view of the torque application part of the torsion test apparatus which concerns on 3rd Embodiment of this invention. It is a top view of a torsion testing device concerning a 4th embodiment of the present invention. It is a top view of a torsion testing device concerning a 5th embodiment of the present invention. It is a top view of a torsion testing device concerning a 6th embodiment of the present invention. It is an external view of the rotation torsion test apparatus which concerns on 7th Embodiment of this invention. FIG. 11 is an external view of a rotary torsion testing device according to an eighth embodiment of the present invention; It is a top view of a tire wear test device according to a ninth embodiment of the present invention. FIG. 20 is an external view of a tire testing device according to a tenth embodiment of the present invention; FIG. 20 is an external view of a tire testing device according to a tenth embodiment of the present invention; FIG. 11 is an external view of a power absorption type endurance test device for an FR transmission according to an eleventh embodiment of the present invention; It is an external view of the power absorption type endurance test apparatus for FF transmissions which concerns on 12th Embodiment of this invention. It is a side view of a torsion testing device according to a thirteenth embodiment of the present invention. FIG. 32 is a side view of a first driving section according to a thirteenth embodiment of the present invention; FIG. 20 is a plan view of a torsion testing device according to a first modified example of the thirteenth embodiment of the present invention; FIG. 20 is a plan view of a torsion testing device according to a second modification of the thirteenth embodiment of the present invention; FIG. 20 is a plan view of a torsion testing device according to a third modified example of the thirteenth embodiment of the present invention; It is a side view of the torsion test apparatus based on 14th Embodiment of this invention. FIG. 20 is an enlarged view of a drive unit according to a fourteenth embodiment of the present invention; It is a top view of the vibration test equipment concerning a 15th embodiment of the present invention. FIG. 20 is a side view of the first actuator according to the fifteenth embodiment of the present invention as seen from the Y-axis direction; FIG. 32 is a top view of a first actuator according to a fifteenth embodiment of the present invention; FIG. 20 is a side view of a table and a third actuator according to a fifteenth embodiment of the present invention as seen from the X-axis direction; FIG. 20 is a side view of a table and a third actuator according to a fifteenth embodiment of the present invention, viewed from the Y-axis direction; FIG. 20 is a block diagram of a control system in a vibration test apparatus according to a fifteenth embodiment of the present invention;

BEST MODE FOR CARRYING OUT THE INVENTION Hereinafter, embodiments of the present invention will be described with reference to the drawings.

(First embodiment)
First, the biaxial output servomotor 150A according to the embodiment of the present invention will be described. FIG. 1 is a side view of the two-axis output servomotor 150A. The two-axis output servomotor 150A is a high output (rated output of 37 kW) ultra-low inertia servomotor having two output shafts 150A2a and 150A2b. The biaxial output servomotor 150A has a body frame 150A1, a drive shaft 150A2, a first bracket 150A3 and a second bracket 150A4.

The body frame 150A1 is a substantially cylindrical frame, and has a stator (not shown) having a coil on its inner periphery. A first bracket 150A3 and a second bracket 150A4 are attached to both ends of the body frame 150A1 in the axial direction so as to close the opening of the body frame 150A1. A motor case is formed by the body frame 150A1, the first bracket 150A3 and the second bracket 150A4. The first bracket 150A3 and the second bracket 150A4 are provided with bearings 150A3b and 150A4b that rotatably support the drive shaft 150A2, respectively. A rotor (not shown) is provided on the outer periphery of the central portion in the longitudinal direction of the drive shaft 150A2. is given a rotational force.

One end 150A2a (right end in FIG. 1) of the drive shaft 150A2 passes through the first bracket 150A3 and protrudes outside from the motor case to form an output shaft 150A2a. The other end 150A2b of the drive shaft 150A2 passes through the second bracket 150A4 and protrudes outside from the motor case to form a second output shaft 150A2b. The second bracket 150A4 incorporates a rotary encoder (not shown) that detects rotation of the other end 150A2b of the drive shaft 150A2.

A pair of tapped holes 150A3t and 150A4t for fixing the biaxial output servomotor 150A are provided on the lower surfaces of the first bracket 150A3 and the second bracket 150A4, respectively. In a conventional servomotor, a fixing tapped hole extending parallel to the drive shaft was provided only on the mounting seat surface (right side in FIG. 1) of the bracket on the load side (the side where the output shaft protrudes). For applications other than precision machine testing, fixing with tapped holes provided in the mounting seat surface of the load side bracket is sufficient. For example, fatigue test equipment and vibration test equipment), when using a high-output servo motor with a rated output of about 10 kW or more, the servo motor may not move in the direction perpendicular to the drive shaft only by fixing the mounting surface of the bracket. could not be completely fixed, for example, vibration with a minute amplitude of several μm to several tens of μm was generated, giving an unignorable error to the test results.

As a result of many vibration analyzes and experiments, the inventors found that by adding two fixing tapped holes extending in the direction perpendicular to the drive shaft on the lower surface of each bracket, vibration noise became noticeable (for example, 1 about an order of magnitude) was found to be improved. In addition to the mounting surface of the load-side bracket, tapped holes are provided on the lower surface of each bracket, and these tapped holes are used to secure the servomotor with bolts, thereby reducing vibration noise and improving machine accuracy. testing becomes possible.

Further, the servomotor 150A has a high rated output of 37 kW and generates a large amount of heat during operation. Two tube joints 150A6 to which external pipes for supplying and discharging cooling water are connected are provided on the upper portion of the body frame 150A1.

In this embodiment, a servomotor unit 150 is used in which the two-axis output servomotor 150A described above and a servomotor 150B having one output shaft 150B2a are connected in series. FIG. 2 is a side view of servo motor unit 150 according to an embodiment of the present invention. The servomotor unit 150 has one drive shaft 152 .

In the following description of the servo motor unit 150, the side where the drive shaft 152 protrudes (the right side in FIG. 2) is called the load side, and the opposite side is called the anti-load side. The 2-axis output servomotor 150A and the servomotor 150B each generate a maximum torque of 350 N・m, and the moment of inertia of the rotating part is suppressed to 10 ⁻² (kg・m ² ) or less, and the rated output is 37 kW. It is a large output ultra-low inertia servo motor.

The servomotor 150B includes a body frame 150B1, a drive shaft 150B2, a load-side bracket 150B3, an anti-load-side bracket 150B4, and a rotary encoder 150B5. The body frame 150B1 and the load-side bracket 150B3 are the same as the body frame 150A1 and the first bracket 150A3 of the two-axis output servomotor 150A. Two tube fittings 150B6 are provided to which the pipes are connected. The anti-load side bracket 150B4 has substantially the same configuration as the second bracket 150A4 of the two-axis output servomotor 150A, but does not have a built-in rotary encoder. externally attached to the A pair of tapped holes 150B3t and 150B4t are also provided on the lower surfaces of the load-side bracket 150B3 and the anti-load-side bracket 150B4, respectively.

One end portion 150B2a on the load side of the drive shaft 150B2 passes through the load side bracket 150B3 and protrudes outside from the motor case to form an output shaft 150B2a. On the other hand, a rotary encoder 150B5 for detecting the angular position of the drive shaft 150B2 is attached to the mounting seat surface (left side surface in FIG. 2) of the anti-load side bracket 150B4, and the other end 150B2b of the drive shaft 150B2 It penetrates the side bracket 150B4 and is housed in the rotary encoder.

As shown in FIG. 2, the output shaft 152B2a of the servomotor 150B and the second output shaft 150A2b of the two-axis output servomotor 150A are connected by a coupling 150C. Also, the load-side bracket 150B3 of the servomotor 150B and the second bracket 150A4 of the two-axis output servomotor 150A are connected with a predetermined gap by a connecting flange 150D.

The connecting flange 150D has a cylindrical trunk portion 150D1 and two flange portions 150D2 extending radially outward from both axial end portions of the trunk portion 150D1. Each flange portion 150D2 is provided with through holes for fixing bolts at positions corresponding to the tapped holes provided in the mounting seat surfaces of the load side bracket 150B3 and the second bracket 150A4. It is bolted to bracket 150A4.

The servomotor unit 150 includes two rotary encoders for detecting the angular position of the drive shaft 150B2 (one built in the second bracket 150A4 of the two-axis output servomotor 150A and one on the opposite side of the servomotor 150B). A rotary encoder 150B5) attached to the bracket 150B4 is provided, but normally only one rotary encoder is used for drive control of the servo motor unit 150, and the other is used for maintenance and monitoring of the drive state.

For example, a vibration test or a durability test (rotational torsion test) of a power transmission device requires a large shaft torque that fluctuates at high speed (high frequency). In order to generate such a large torque that fluctuates at a high frequency, a motor with a small inertia moment of the rotor and a large capacity (high output) is required. To realize such a servomotor, the rotor must be elongated. However, if the rotor is elongated beyond a certain extent, the rigidity of the rotor (rotating shaft) is lowered, and the vibration of the rotor such as warping in a bow shape becomes noticeable, and the motor cannot operate normally. Therefore, in the conventional structure in which the rotating shaft is supported only at both ends by a pair of bearings, there is a limit to increasing the capacity while maintaining a low moment of inertia.

In the servomotor unit 150 of this embodiment, the long rotor connected by the coupling 150C is supported by bearings at both ends in the longitudinal direction and at two points near the connecting portion. , Even if the rotor length is increased, it is possible to maintain high rigidity and operate stably. This makes it possible to generate large torque that fluctuates at high frequencies, which was not possible with conventional servomotors. Became. For example, an angular acceleration of 30000 rad/s ² or more can be achieved with the servo motor unit 150 alone (no load state).

The servo motor unit 150 of this embodiment is configured to connect two servo motors (two motor cases and two rotary shafts), but as shown in FIG. One or more bearings may be provided in the middle of the longitudinal direction, and the drive shaft may be pivotally supported at both ends and at one or more points in the middle.

Next, the configuration of the rotary torsion testing device 1 according to the first embodiment of the present invention will be described. FIG. 4 is a side view of the rotary torsion testing device 1 according to the first embodiment of the present invention. The rotary torsion test apparatus 1 is a device for performing a rotary torsion test using an automobile clutch as a test piece T1. A fixed or variable torque set between can be applied. The rotary torsion test apparatus 1 includes a frame 10 that supports each part of the rotary torsion test apparatus 1, a load application unit 100 that applies a predetermined torque to the test piece T1 while rotating together with the test piece T1, and the load application unit 100 that is rotatable. bearings 20, 30 and 40 that support the load application unit 100; slip ring units 50 and 60 that electrically connect the inside and outside of the load application unit 100; a rotary encoder 70 that detects the number of rotations of the load application unit 100; 100 is provided with an inverter motor 80, a drive pulley 91, and a drive belt (timing belt) 92 for rotating in a set rotation direction and number of rotations.

The pedestal 10 has a lower base plate 11 and an upper base plate 12 horizontally arranged vertically, and a plurality of vertical support walls 13 connecting the lower base plate 11 and the upper plate 12 . A plurality of anti-vibration mounts 15 are attached to the lower surface of the lower base plate 11 , and the frame 10 is arranged on a flat floor F via the anti-vibration mounts 15 . An inverter motor 80 is fixed to the upper surface of the lower base plate 11 . Bearings 20 , 30 , 40 and a rotary encoder 70 are attached to the upper surface of the upper base plate 12 .

FIG. 5 is a vertical cross-sectional view of the load application unit 100 of the rotary torsion test apparatus 1. FIG. The load applying unit 100 includes a stepped cylindrical casing 100a, a servo motor unit 150, a speed reducer 160, a connecting shaft 170, and a torque sensor 172 mounted inside the casing 100a. The casing 100a includes a motor housing portion (body portion) 110 housing the servo motor unit 150, a shaft portion 120 rotatably supported by the bearing portion 20, and a shaft portion 130 rotatably supported by the bearing portion 30. and a shaft portion 140 to which the slip ring 51 of the slip ring portion 50 (FIG. 4) is attached. The motor housing portion 110 and the shaft portions 120, 130 and 140 are substantially cylindrical members each having a hollow portion (or a stepped cylindrical member whose diameter changes stepwise in the axial direction). The motor accommodating portion 110 is a member with the largest outer diameter that accommodates the servo motor unit 150 in its hollow portion. A shaft portion 120 is connected to one end portion (right end portion in FIG. 5) of the motor accommodating portion 110 on the test piece T1 side, and a shaft portion 130 is connected to the other end portion. A shaft portion 140 is connected to the end portion of the shaft portion 130 opposite to the motor accommodating portion 110 . The shaft portion 140 is rotatably supported by the bearing portion 40 at the tip portion (the left end portion in FIG. 4).

As shown in FIG. 5 , the servomotor unit 150 is fixed to the motor housing portion 110 by a plurality of fixing rods 111. As shown in FIG. Each fixed rod 111 has a tapped hole 150B3t provided in the load side bracket 150B3 of the servomotor 150B, a tapped hole 150B4t provided in the anti-load side bracket 150B4, and a first bracket of the two-axis output servomotor 150A, as shown in FIG. It is screwed into a tapped hole 150A3t provided in 150A3 and a tapped hole 150A4t provided in the second bracket 150A4.

A drive shaft 152 of the servomotor unit 150 is connected to an input shaft of a speed reducer 160 via a coupling 154 . A connecting shaft 170 is connected to the output shaft of the speed reducer 160 . The speed reducer 160 has a mounting flange 162. With the mounting flange 162 sandwiched between the motor housing portion 110 and the shaft portion 120, the motor housing portion 110 and the shaft portion 120 are connected by bolts (not shown). is fixed to the casing 100a by tightening the .

The shaft portion 120 is a substantially stepped cylindrical member, has a pulley portion 121 with a large outer diameter on the side of the motor housing portion 110, and has a main shaft portion 122 rotatably supported by the bearing portion 20 on the side of the test piece T1. have As shown in FIG. 4, a drive belt 92 is wound around the outer peripheral surface of the pulley portion 121 and a drive pulley 91 attached to the drive shaft 81 of the inverter motor 80, so that the drive force of the inverter motor 80 is The force is transmitted to the pulley portion 121 by the drive belt 92, and the load applying portion 100 rotates. Further, the connecting portion between the speed reducer 160 and the connecting shaft 170 is accommodated in the pulley portion 121 . A compact device structure is realized without increasing the number of parts by using the portion where the outside diameter needs to be thickened to accommodate the connecting portion as a pulley.

A torque sensor 172 is attached to the tip portion (the right end portion in FIG. 5) of the main shaft portion 122 of the shaft portion 120 . One surface of the torque sensor 172 (the right side surface in FIG. 5) is a seat surface for mounting the input shaft (clutch cover) of the test piece T1, and the torque sensor 172 detects the torque applied to the test piece T1. .

Bearings 123 and 124 are provided near both ends in the axial direction on the inner peripheral surface of the main shaft portion 122 of the shaft portion 120 . The connecting shaft 170 is rotatably supported within the shaft portion 120 by bearings 123 and 124 . The torque sensor 172 is formed in a substantially cylindrical shape having a hollow portion, and the distal end portion (the right end portion in FIG. 5) of the connecting shaft 170 penetrates the hollow portion of the torque sensor 172 and protrudes to the outside. The tip protruding from the torque sensor 172 is inserted into and fixed to the shaft hole of the clutch disk (clutch hub), which is the output shaft of the test piece T1. That is, by rotating the connecting shaft 170 with respect to the casing 100a of the load applying unit 100 by the servomotor unit 150, the input shaft (clutch cover) of the test piece T1 fixed to the casing 100a and the connecting shaft 170 are fixed. A set dynamic or static torque can be applied between the output shaft (clutch disc) of the test piece T1 thus set.

Further, as shown in FIG. 4, a rotary encoder 70 for detecting the number of rotations of the load applying section 100 is arranged near the end of the shaft section 130 (the left end in FIG. 4).

A slip ring 51 of the slip ring portion 50 is attached to the center portion of the shaft portion 140 in the axial direction. The slip ring 51 is connected to a power line 150 W ( FIG. 5 ) that supplies drive current to the servo motor unit 150 . A power line 150 W extending from the servo motor unit 150 is connected to the slip ring 51 through hollow portions formed in the shaft portions 130 and 140 .

The slip ring section 50 includes a slip ring 51 , brush fixtures 52 and four brushes 53 . As described above, the slip ring 51 is attached to the shaft portion 140 of the load applying portion 100 . Also, the brush 53 is fixed to the bearing portion 40 by a brush fixture 52 . The slip ring 51 has four electrode rings 51r arranged at equal intervals in the axial direction, and each brush 53 is arranged to face each electrode ring 51r. Each power line 150W of the servo motor unit 150 is connected to each electrode ring 51r, and each brush 53 is connected to a servo motor drive unit 330 (described later). That is, each power line 150W of the servomotor unit 150 is connected to the servomotor drive unit 330 via the slip ring portion 50 . The slip ring section 50 introduces the driving current of the servo motor unit 150 supplied from the servo motor driving unit 330 into the rotating load applying section 100 .

A slip ring (not shown) of the slip ring portion 60 is attached to the tip portion (the left end portion in FIG. 4) of the shaft portion 140 . A communication line 150W' (FIG. 5) extending from the servo motor unit 150 is connected to the slip ring of the slip ring portion 60. For example, a torque sensor 172 or a rotary encoder 150B5 (FIG. 2) incorporated in the servo motor unit 150 is connected. ) are output to the outside via the slip ring portion 60 . When a large current such as a driving current for a large-capacity motor is passed through the slip ring, large electromagnetic noise is likely to occur due to discharge. Also, slip rings are not well shielded and are susceptible to electromagnetic noise interference. As described above, the communication line 150W' through which a weak current flows and the power line 150W through which a large current flows are connected to the external wiring using separate slip rings arranged at a constant distance. Noise is effectively prevented from being mixed into communication signals. In addition, in the present embodiment, the slip ring portion 60 is provided on the surface of the bearing portion 40 opposite to the slip ring portion 50 side. With this configuration, the effect of shielding the slip ring portion 60 from electromagnetic noise generated in the slip ring portion 50 by the bearing portion 40 is also obtained.

Next, the control system of the rotary torsion testing device 1 will be described. FIG. 6 is a block diagram showing a schematic configuration of a control system of the rotary torsion testing device 1. As shown in FIG. The rotary torsion test apparatus 1 includes a control unit C1 that controls the entire rotary torsion test apparatus 1, a setting unit 370 for setting test conditions, and the set test conditions (waveform of torque and torsion angle applied to the test piece etc.) to calculate the waveform of the drive amount of the servo motor unit 150 and output it to the control unit C1; A drive unit 330, an inverter motor drive unit 340 that generates drive current for the inverter motor 80 based on the control of the control unit C1, and a torque measurement that calculates the torque applied to the test piece based on the signal from the torque sensor 172. A unit 350 and a rotational speed measurement unit 360 for calculating the rotational speed of the load applying section 100 based on the signal from the rotary encoder 70 are provided.

The setting unit 370 includes a user input interface such as a touch panel (not shown), a replaceable recording media reader such as a CD-ROM drive, an external input interface such as GPIB (General Purpose Interface Bus) and USB (Universal Serial Bus), and It has a network interface. The setting unit 370 accepts user input received via a user input interface, data read from a removable recording medium, data input from an external device (e.g., function generator) via an external input interface, and/or a network interface. Test conditions are set based on the data obtained from the server via In addition, the rotational torsion test apparatus 1 of the present embodiment detects the torsion applied to the specimen T1 by the torsion angle applied to the specimen T1 (that is, the servo motor unit detected by the rotary encoder 150B5 incorporated in the servo motor unit 150 150 drive amount) and torque control based on the torque applied to the test piece T1 (that is, detected by the torque sensor 172). , can be set by the setting unit 370 which control method is to be used.

The control unit C1 commands the inverter motor drive unit 340 to rotate the inverter motor 80 based on the setting value of the rotation speed of the test piece T1 acquired from the setting unit 370. FIG. The control unit C1 also commands the servo motor drive unit 330 to drive the servo motor unit 150 based on the waveform data of the drive amount of the servo motor unit 150 acquired from the waveform generation unit 320 .

As shown in FIG. 6 , the torque measurement value calculated by the torque measurement unit 350 based on the signal from the torque sensor 172 is sent to the control unit C 1 and the waveform generation unit 320 . A signal from a built-in rotary encoder built in the servo motor unit 150 is sent to the control unit C1, the waveform generation unit 320 and the servo motor drive unit 330. FIG. The waveform generation unit 320 calculates the measured value of the number of revolutions of the servo motor unit 150 from the signal of the built-in rotary encoder that detects the rotation angle of the drive shaft 152 of the servo motor unit 150 . The waveform generation unit 320 compares the set value and the measured value of the torque (in the case of displacement control, the amount of drive of the servo motor unit 150) in the case of torque control, and sends a signal to the control unit C1 so that the two match. Correct the set value of the driving amount of the servo motor unit 150 to be sent.

Further, the measured value of the number of revolutions of the load applying section 100 calculated by the number of revolutions measuring unit 360 based on the signal from the rotary encoder 70 is sent to the control unit C1. The control unit C1 compares the set value and the measured value of the number of revolutions of the load applying section 100, and feedback-controls the frequency of the drive current sent to the inverter motor 80 so that the two match.

Also, the servo motor drive unit 330 compares the target value of the drive amount of the servo motor unit 150 with the drive amount detected by the built-in rotary encoder 150B5, and adjusts the servo motor unit 150 so that the drive amount approaches the target value. feedback control of the drive current to be sent to

In addition, the control unit C1 has a hard disk drive (not shown) for storing test data, and the rotation speed of the test piece T1, the torsion angle applied to the test piece T1 (the rotation angle of the servo motor unit 150) and the data of each measurement value of the torsional load are recorded in the hard disk device. The time variation of each measured value is recorded over the entire period from the start to the end of the test. With the configuration of the first embodiment described above, a rotational torsion test is performed using an automobile clutch as the specimen T1.

In the rotational torsion test apparatus 1 described above, the output of the inverter motor 80 for controlling the rotation speed and the output of the servo motor unit 150 for controlling the torque are coupled, so that the rotation speed and the torque can be controlled independently and with high accuracy. It is configured. In particular, by newly adopting a servo motor unit 150 in which a plurality of ultra-low inertia servo motors are connected in series, it becomes possible to control a large torque that fluctuates with a high angular jerk (angular jerk). output (in particular, torque oscillation of a reciprocating engine) can be reproduced accurately. Also, by using the servo motor unit 150, the responsiveness of torque control is improved, and a response time of 3 ms or less is achieved. The rotary drive device having such a configuration can be used as a power source for not only the rotary torsion test device but also various devices. In particular, it can be used as a power simulator (simulated engine) capable of outputting power simulating various types of engine outputs in an automobile (or automobile parts) test apparatus. Further, since the torque generated by the servo motor unit 150 is controlled with high precision, the reproducibility is extremely high and there is no individual difference. Therefore, it is possible to apply a more uniform load than in conventional tests using an actual engine, enabling tests with higher reproducibility.

(Modified example of the first embodiment)
7 and 8 are external views of power simulators 1a and 1b obtained by partially modifying the rotational torsion testing apparatus 1 according to the first embodiment of the present invention described above, respectively.

A power simulator 1a shown in FIG. 7 differs from the rotational torsion test apparatus 1 in that it includes a bearing portion 1020, a slip ring 1401 and a mounting portion 173. FIG. The bearing portion 1020 has the same configuration as the bearing portion 1020 of the second embodiment, which will be described later, and incorporates a torque sensor that detects the torque of the connecting shaft 170 (connecting shaft 1170 in the second embodiment). The slip ring 1401 is attached to the bearing portion 1020, and extracts the signal output from the torque sensor incorporated in the bearing portion 1020 to the outside. The attachment portion 173 is a flange joint and is attached to the tip portion of the connecting shaft 170 . The power simulator 1a configured in this manner includes engine accessories (for example, damper pulleys, alternators, balance shafts, starter motors, ring gears, water pumps, oil pumps, chains, timing belts, couplings, VCTs), Used for endurance testing of power transmission devices, tires, etc.

Further, in the rotational torsion test apparatus 1 and the power simulator 1a described above, the inverter motor 80 is arranged on the lower base plate 11, and the load applying unit 100 is arranged on the upper base plate 12, which is a two-stage structure. However, as in the power simulator 1b shown in FIG. 8, a one-stage structure in which the inverter motor 80 and the load applying section 100 are arranged on the same base plate 10X may be employed. Note that the two-stage structure is effective in reducing the installation area. In addition, the single-stage structure is advantageous in terms of cost reduction due to its simple structure, and is advantageous in improving the rigidity of the base (that is, vibration resistance and load resistance).

Next, a specific example of an endurance test apparatus for engine accessories using the power simulator 1a will be described. The test apparatus 100E described below is for a starter motor that performs an endurance test by applying a rotational driving force simulating an engine load generated by a power simulator 1a to a ring gear T1 of a flywheel and a starter motor T2, which are specimens. test equipment. The test apparatus 100E holds the starter motor and the ring gear of the flywheel in an engaged state, applies the rotational driving force of the power simulator 1a to them, and performs an endurance test of the starter motor and the ring gear.

FIG. 9 is a side view of the test device 100E. FIG. 10 is an enlarged view of the vicinity of the specimen (ring gear T1, starter motor T2).

As shown in FIGS. 9 and 10, the test apparatus 100E is obtained by adding a support section S for holding a test piece to the power simulator 1a. That is, the test apparatus 100E includes an inverter motor 80 attached to the lower base plate 11 of the gantry 10, and a load application unit 100 rotatably supported by bearings 1020, 30, and 40 attached to the upper base plate 12. I have. The load applying unit 100 is rotationally driven by the inverter motor 80 . A servo motor unit 150 and a speed reducer are incorporated in the load applying unit 100, and the output shaft of the servo motor unit 150 is connected to a connecting shaft 170 protruding outside the load applying unit 100 via the speed reducer. The connecting shaft 170 is arranged coaxially with the rotating shaft of the load applying section 100 , and the rotation of the connecting shaft 170 is the rotation of the load applying section 100 by the inverter motor 80 plus the rotation of the servo motor unit 150 . . The inverter motor 80 reproduces the rotation speed of the engine, and the servo motor unit 150 reproduces the high-speed fluctuating torque of the engine (high angular acceleration, high angular jerk (angular jerk)).

A mounting portion 173 for mounting the ring gear T1 is attached to the distal end portion of the connecting shaft 170 of the load applying portion 100 . A support portion S for supporting the starter motor T2 is attached to the upper base plate 12 of the frame 10 . When the ring gear T1 is attached to the attachment portion 173 and the starter motor T2 is attached to the support portion S, the ring gear T1 and the pinion gear of the starter motor T2 are engaged. In this state, the test is performed by driving the power simulator 1a of the test device 100E to give rotation simulating engine rotation to the ring gear T1 and the starter motor T2.

(Second embodiment)
Next, a power circulation type rotary torsion testing device 1000 according to a second embodiment of the present invention will be described. A rotational torsion test apparatus 1000 is an apparatus for performing a rotational torsion test using an automobile propeller shaft as a test piece T2. can be added. FIG. 11 is a plan view of the rotary torsion testing apparatus 1000, and FIG. 12 is a side view of the rotary torsion testing apparatus 1000 (viewed from the bottom to the top in FIG. 11). Also, FIG. 13 is a vertical cross-sectional view of the vicinity of a load applying section 1100, which will be described later. The control system of the rotary torsion testing device 1000 has the same schematic configuration as that of the first embodiment shown in FIG .

As shown in FIG. 11, the rotary torsion test apparatus 1000 includes four bases 1011, 1012, 1013, and 1014 that support each part of the rotary torsion test apparatus 1000, and the two ends of the test piece T2 while rotating together with the test piece T2. a load applying section 1100 that applies a predetermined torque to the load applying section 1100; bearing sections 1020, 1030 and 1040 that rotatably support the load applying section 1100; a slip ring section 1050 that electrically connects wiring inside and outside the load applying section 1100; 1060 and 1400, a rotary encoder 1070 for detecting the number of rotations of the load applying section 1100, the load applying section 1100 and one end (the right end in FIG. 11) of the test piece T2 are rotationally driven in a set rotation direction and number of rotations. a driving force transmission unit 1190 (a driving pulley 1191, a driving belt (timing belt) 1192 and a driven pulley 1193) that transmits the driving force of the inverter motor 1080 to the load applying unit 1100, and the driving force of the inverter motor 1080 to one end of the specimen T2. The driving force transmission portion 1200 includes a bearing portion 1210, a drive shaft 1212, a relay shaft 1220, a bearing portion 1230, a drive shaft 1232, a drive pulley 1234, a bearing portion 1240, a drive shaft 1242, a driven pulley 1244, and a drive belt (timing belt) 1250. and a workpiece mounting portion 1280 .

The bearings 1020, 1030, 1040, the slip ring part 1050, the slip ring part 1060, the rotary encoder 1070, the inverter motor 1080, and the drive pulley 1091 in the rotary torsion test device 1000 are each the rotary torsion test device 1 of the first embodiment. , the bearings 20, 30, 40, the slip ring 50, the slip ring 60, the rotary encoder 70, the inverter motor 80, and the drive pulley 91. Moreover, the load applying section 1100 has the same configuration as the load applying section 100 of the first embodiment, except for a shaft section 1120, a connecting shaft 1170, a work mounting section 1180, and a slip ring section 1400 which will be described later. Further, the drive belt 1192 differs from the drive belt 92 of the first embodiment in that it is hooked on a driven pulley 1193 on the driven side, but the other structures are the same as the drive belt 92 . In the following description of the second embodiment, the same or similar reference numerals are used for configurations that are the same as or similar to those of the first embodiment, and detailed description is omitted, and differences in configuration from the first embodiment are described. Mainly explained.

The four bases 1011, 1012, 1013 and 1014 are arranged on the same flat floor F and fixed by fixing bolts (not shown). An inverter motor 1080 and a bearing 1210 are fixed on the base 1011 . Bearings 1020 , 1030 and 1040 that support the load application section 1100 and a support frame 1402 for the slip ring section 1400 are fixed on the base 1012 . A bearing portion 1230 is fixed to the base 1013 and a bearing portion 1240 is fixed to the base 1014 . The bases 1013 and 1014 can be moved in the axial direction of the bearing 1230 or 1240 according to the length of the specimen T1 by loosening the respective fixing bolts.

The connecting shaft 1170 of the load applying portion 1100 protrudes outside from the tip portion (the right end in FIG. 13) of the shaft portion 1120, and the tip portion (the right end in FIG. 13) of the connecting shaft 1170 has a work mounting portion (flange joint ) 1180 is fixed. A slip ring 1401 having a plurality of electrode rings is attached to the central portion in the axial direction of the portion protruding from the shaft portion 1120 of the connecting shaft 1170 .

Further, as shown in FIG. 13, an annular constricted portion 1172 having a small outer diameter is formed in the portion of the connecting shaft 1170 that is accommodated in the shaft portion 1120, and the peripheral surface of the constricted portion 1172 is attached with a strain gauge 1174 . The connecting shaft 1170 is a cylindrical member having a hollow portion (not shown) penetrating on the central axis, and an insertion hole (not shown) communicating with the hollow portion is formed in the constricted portion 1172 . A lead (not shown) of the strain gauge 1174 is passed through the through hole and the hollow portion formed in the connecting shaft 1170 and connected to each electrode ring of the slip ring 1401 . Instead of the hollow portion and the insertion hole, a wiring groove extending from the constricted portion 1172 to the slip ring 1401 is provided on the peripheral surface of the connecting shaft 1170, and the lead of the strain gauge 1174 is wired through the wiring groove to the slip ring 1401. may be configured.

A brush portion 1403 fixed on a support frame 1402 is arranged below the slip ring 1401 . The brush portion 1403 includes a plurality of brushes arranged facing each other so as to contact each electrode ring of the slip ring 1401 . A terminal of each brush is connected to a torque measuring unit 1350 (described later) by a wire (not shown).

Next, the configuration of driving force transmission section 1200 (FIG. 11) will be described. Bearings 1210, 1230 and 1240 rotatably support drive shafts 1212, 1232 and 1242, respectively. One end of drive shaft 1212 (the left end in FIG. 11) is connected to the drive shaft of inverter motor 1080 via drive pulley 1191 . One end of drive shaft 1232 (the left end in FIG. 11) is connected to the other end of drive shaft 1212 (the right end in FIG. 11) via relay shaft 1220 . A drive pulley 1234 is attached to the other end of the drive shaft 1232 (right end in FIG. 11), and a driven pulley 1244 is attached to one end of the drive shaft 1242 (right end in FIG. 11). A drive belt 1250 is stretched between the drive pulley 1234 and the driven pulley 1244 . A workpiece attachment portion (flange joint) 1280 is attached to the other end of the drive shaft 1242 (the left end in FIG. 11) for fixing one end of the specimen T2.

The driving force of inverter motor 1080 is transmitted through driving force transmission section 1200 (that is, drive shaft 1212, relay shaft 1220, drive shaft 1232, drive pulley 1234, drive belt 1250, driven pulley 1244, and drive shaft 1242). It is transmitted to the work mounting portion 1280 to rotate the work mounting portion 1280 in the set rotation direction and rotation speed. At the same time, the driving force of the inverter motor 1080 is transmitted to the load applying portion 1100 via the driving force transmitting portion 1190 (that is, the driving pulley 1191, the driving belt 1192 and the driven pulley 1193). 1280 are rotated synchronously (that is, always at the same number of revolutions and the same phase).

(Third embodiment)
In the above-described second embodiment, the drive shaft 1212 and the load applying section 1100, and the drive shaft 1232 and the drive shaft 1242, which are arranged parallel to each other, are connected by drive belts 1192 and 1250, respectively, to form a power circulation system. there is However, the present invention is not limited to this configuration, and configurations in which power is transmitted using a gear device instead of a drive belt, as in third to seventh embodiments described below, are also included within the scope of the present invention. be

FIG. 14(a) is a top view of a torsion testing device according to a third embodiment of the present invention. Moreover, FIG.14(b) is a side view of the torsion test apparatus which concerns on this embodiment. As shown in FIG. 14, the torsion testing apparatus 100 of this embodiment has a workpiece rotating servo motor 121, a torque applying unit 130, a first gear box 141, and a second gear box 142 fixed on a base 110. It has a configuration.

The first gearbox 141 has four axial connections 141a1, 141a2, 141b1 and 141b2. The second gearbox 142 also has two axial connections 142a and 142b.

A drive pulley 122 is attached to the output shaft 121a of the servomotor 121 for rotating the workpiece. A shaft 123a of the driven pulley 123 is attached to the shaft connecting portion 141a1 of the first gear box 141. As shown in FIG. An endless belt 124 is wound around the drive pulley 122 and the driven pulley 123. By driving the workpiece rotating servo motor 121, the driven pulley 123 can be rotated at a desired rotational speed. .

A torque applying unit 130 is connected to the axial connection portions 141b1 and 141b2. The configuration of the torque applying unit 130 will be described below.

FIG. 15 is a side sectional view of the torque applying unit 130 and the first gearbox 141 of this embodiment. The torque applying unit 130 includes a casing 131 , and a torque applying servomotor unit 132 and a speed reducer 133 fixed in the casing 131 . The torque applying servomotor unit 132 has the same configuration as the servomotor unit 150 of the first embodiment, but instead of the servomotor unit 150, the servomotor 150B of the first embodiment is used alone. good too. A tubular portion 131a is formed on one axial end side (right side in the figure) of the casing 131 . The tubular portion 131a is inserted into the first gear box 141 via the shaft connecting portion 141b1 and is rotatably supported within the first gear box 141. As shown in FIG. A gear 141b3 is attached to the tubular portion 131a.

The speed reducer 133 has an input shaft 133a and an output shaft 133b, and reduces rotational motion input to the input shaft 133a and outputs it to the output shaft 133b. An input shaft 133a of the speed reducer 133 is connected to an output shaft 132a of a torque applying servomotor unit 132 by a coupling 134 . An output shaft 133b of the speed reducer 133 is rotatably supported inside the tubular portion 131a of the casing 131 and protrudes from the tip of the tubular portion 131a. The output shaft 133b of the speed reducer 133 protruding from the tubular portion 131a is connected to the shaft connecting portion 141b2 of the first gearbox 141. As shown in FIG.

As shown in FIG. 14, the output shaft 133b of the speed reducer 133 is connected through a coupling 151 to the input shaft W1a of the transmission unit W1 to be tested. The output shaft W1b of the transmission unit W1 is connected to the shaft connecting portion 142b of the second gearbox 142 via the torque sensor 160. As shown in FIG.

An output shaft W2b of the transmission unit W2 is connected via a relay shaft 143 to the shaft connection portion 142a of the second gearbox 142 . An input shaft W2a of the transmission unit W2 is connected to the shaft connecting portion 141a2 of the first gearbox 141 via a coupling 152. As shown in FIG.

Here, the shaft 123 a of the driven pulley 123 attached to the shaft connecting portion 141 a 1 of the first gear box 141 and the shaft attached to the shaft connecting portion 141 a 2 are connected through the coupling 153 inside the first gear box 141 . are connected to each other and are configured to rotate together. A gear 141a3 is attached to the shaft 123a of the driven pulley 123 attached to the shaft connection portion 141a1. A gear 141b3 is attached inside the first gear box 141 to the tubular portion 131a connected to the shaft connection portion 141b1. As shown in FIG. 14(a), the gear 141a3 and the gear 141b3 are meshed via an intermediate gear 141i, and the shaft connected to the shaft connection portions 141a1 and 141a2 and the shaft connected to the shaft connection portion 141b1 It is possible to transmit rotational motion to each other. Since the intermediate gear 141i is interposed between the gear 141a3 and the gear 141b3, the driven pulley 123, the relay shaft 143, and the casing 131 of the torque applying unit 130 rotate in the same direction.

A gear 142a1 is attached to the shaft (one end of the relay shaft 143) connected to the shaft connecting portion 142a. A gear 142b1 is connected to the shaft connected to the shaft connecting portion 142b. The gears 142a1 and 142b1 mesh via an intermediate gear 142i inside the second gear box 142, and between the shaft connected to the shaft connection portion 142a and the shaft connected to the shaft connection portion 142b, They are capable of transmitting rotational motion to each other. Since the intermediate gear 142i is interposed between the gears 142a1 and 142b1, the shaft connected to the shaft connection portion 142a and the shaft connected to the shaft connection portion 142b are rotated in the same direction. It's becoming

Therefore, in this embodiment, when the workpiece rotating servomotor 121 (FIG. 14) is driven, the driven pulley 123 and the casing 131 (FIG. 15) connected to the driven pulley 123 via gears are driven to rotate. It will be. As described above, since the torque-applying servomotor unit 132 is fixed to the casing 131, the casing 131 and the torque-applying servomotor rotate together. Therefore, when the torque-applying servomotor unit 132 is driven while the casing 131 is rotating, the output shaft 133b of the speed reducer 133 is controlled by the rotational speed of the casing 131 and the output shaft 133b by the torque-applying servomotor unit 132. will rotate at the number of rotations added to the number of rotations of

The transmission unit W2 is of the same type (same speed reduction ratio) as the transmission unit W1. Also, the gear ratios of gearboxes 141 and 142 are both 1:1. Therefore, the rotational speeds of the shafts connected to the shaft connection portions 141a2 and 141b2 of the first gearbox 141 are substantially equal. The transmission unit W2 is a kind of dummy work used for adjusting the rotational speed of the shafts connected to the shaft connection portions 141a2 and 141b2 as described above, and is not subject to the torsion test.

In this embodiment, for example, the workpiece rotating servomotor 121 is driven at a constant speed, and the output shaft 132a is reciprocatingly driven by the torque applying servomotor unit 132 (FIG. 15), thereby rotating the input shaft W1a of the transmission unit W1. It is possible to apply a torque that periodically fluctuates while rotating.

(Fourth embodiment)
Next, a fourth embodiment of the invention will be described. FIG. 16 is a top view of a torsion testing device according to a fourth embodiment of the present invention; As shown in FIG. 16, the torsion testing apparatus 100A of this embodiment does not use a dummy work, and the coupling 152 and the axial connection portion 142a of the second gearbox 142 are directly connected by the relay shaft 143A. Except for this, it is the same as the torsion test device 100 of the third embodiment. In the following description of the fourth embodiment, elements having the same or similar functions as those of the third embodiment are denoted by the same or similar reference numerals, and overlapping descriptions are omitted.

In the present embodiment, the number of rotations of the relay shaft 143A (ie, the number of rotations of the casing 131 of the torque applying unit 130) and the number of rotations of the shaft connected to the shaft connection portion 141b2 of the first gearbox 141 (ie, the transmission The number of revolutions of the input shaft W1a of the unit W1) is different. Therefore, in this embodiment, the torque applying servomotor unit 132 (FIG. 15) of the torque applying unit 130 is rotationally driven so as to compensate for the change in the rotational speed of the input/output shaft of the transmission unit W1. For example, if the reduction ratio of the transmission unit W1 is 1/3.5, the rotation speed of the input shaft W1a is 4000 rpm, and the rotation speed of the output shaft W1b is 1143 rpm, the torsion test is performed. The rotation speed of the work rotation servomotor 121 is set so that the torque is imparted to the casing 131, and the rotation speed of the torque imparting servomotor unit 132 is set so that the relative rotation speed of the output shaft 133b of the reduction gear 133 with respect to the casing 131 is 2857 rpm. can set the rotation speed of the input shaft W1a of the transmission unit W1 to 4000 rpm.

Thus, in this embodiment, the torsion test of the transmission unit W1 can be performed while circulating the power without using a dummy work.

In addition, in this embodiment, since the workpiece is rotationally driven and torqued by a highly responsive servomotor, it is possible to change the gear ratio of the transmission unit W1 during the torsion test. be. That is, in the present embodiment, it is possible to rapidly change the rotation speed of the torque applying servomotor unit 131 in synchronism with the change in the rotation speed of the output shaft W1b due to the gear ratio change of the transmission unit W1. Even if the gear ratio of the unit W1 is changed, the gears in the gear boxes 141 and 142 and the transmission unit W1 will not be damaged by an excessive load.

(Fifth embodiment)
In the third and fourth embodiments of the present invention, the transmission unit is used as the subject (work). However, the present invention is not limited to the above configuration, and it is also possible to perform torsion tests on other types of works. A torsion test apparatus according to a fifth embodiment of the present invention, which will be described below, performs a torsion test using the entire power transmission system of an FR vehicle as a work.

FIG. 17 is a top view of a torsion testing device according to a fifth embodiment of the present invention; As shown in FIG. 17, the torsion testing device 100B according to the present embodiment performs a torsion test on a power transmission system W3 of an FR vehicle, which is composed of a transmission unit TR1, a propeller shaft PS, and a differential gear DG1. be.

Since the torsion testing apparatus 100B of the present embodiment has two systems (DG1a, DG1b) of output shafts of the differential gear DG1, second gearboxes (142B1, 142B2) for returning the output of the differential gear DG1 to the first gearbox 141B ) and two relay shafts (143B1, 143B2) are provided. Specifically, output shafts DG1a and DG1b of the differential gear DG1 are connected to relay shafts 143B1 and 143B2 via second gear boxes 142B1 and 142B2, respectively.

Further, the first gearbox 141B includes axial connection portions 141Bb1 and 141Bb2 (axial connection portions 141b1 and 141b2 in the third embodiment) to which the tubular portion 131a of the casing 131 of the torque applying unit 130 and the input shaft TR1a of the transmission unit TR1 are respectively attached. ), shaft connection portions 141Ba1 and 141Ba2 to which the output shaft 121a of the workpiece rotation servomotor 121 and the relay shaft 143B1 are connected, and a shaft connection portion 143Bc to which the relay shaft 143B2 is connected. Further, the output shaft 121a of the workpiece rotating servomotor 121 and the relay shaft 143B1 are connected via a coupling 153B arranged inside the first gear box 141. As shown in FIG. Furthermore, the input shaft TR1a of the transmission unit TR1 and the output shaft 133b of the reduction gear 133 of the torque applying unit 130 are connected via a coupling 151B arranged inside the first gearbox 141. FIG.

The shafts connected to the shaft connection portions 141Ba1, 141Bb1, and 141Bc are connected to each other via gears and intermediate gears (not shown) separately attached to each shaft. , the relay shafts 143B1 and 143B2 and the casing 131 of the torque applying unit 130 rotate.

In the present embodiment, as in the fourth embodiment, the rotational speed of the input shaft TR1a of the transmission unit TR1 and the rotational speed of the relay shafts 143B1 and 143B2 are different. 131 (Fig. 15).

(Sixth embodiment)
Further, in the configuration of the present invention, it is also possible to use a power transmission system for an FF vehicle as the work. A torsion test apparatus according to a sixth embodiment of the present invention, which will be described below, performs a torsion test on the power transmission system of an FF vehicle.

FIG. 18 is a top view of a torsion testing device 100C according to the sixth embodiment of the present invention. As shown in FIG. 18, the torsion test device 100C of the present embodiment performs a torsion test using a power transmission system W4 for an FF vehicle, in which a transmission unit TR2 incorporating a torque converter TC and a differential gear DG2 are integrated, as a work. It is something to do.

As shown in FIG. 18, the power transmission system W4 is a power transmission system for a transverse engine in which the input shaft TR2a of the transmission unit TR2 and the output shafts DG2a and DG2b of the differential gear DG2 are formed substantially parallel. be. Therefore, in this embodiment, one output shaft DG2a of the differential gear DG2 is directly connected to the first gearbox 141C, and only the other output shaft DG2b is connected to the relay shaft 143C via the second gearbox 142C. are doing.

As in the fifth embodiment, the first gearbox 141C of the present embodiment includes axial connection portions 141Cb1 and 141Cb2 to which the tubular portion 131a of the casing 131 of the torque applying unit 130 and the input shaft TR2a of the transmission unit TR2 are respectively attached, and a work piece. It has shaft connection portions 141Ca1 and 141Ca2 to which the output shaft 121a of the rotation servomotor 121 and the output shaft DG2a of the differential gear DG2 are connected, and a shaft connection portion 143Cc to which the relay shaft 143C is connected. The output shaft 121a of the workpiece rotating servomotor 121 and the output shaft DG2a of the differential gear DG2 are connected by a coupling 153C arranged in the first gear box 141C. Also, the output shaft 133b of the speed reducer 133 of the torque applying unit 130 and the input shaft TR2a of the transmission unit TR2 are connected by a coupling 151C arranged inside the first gear box 141C.

The shafts connected to the shaft connection portions 141Ca1, 141Cb1, and 141Cc are connected to each other via gears separately attached to each shaft. When the work rotation servo motor 121 is driven, the output shaft DG2a of the differential gear DG2 , the relay shaft 143C and the casing 131 of the torque applying unit 130 are rotated.

Further, in the present embodiment, as in the fourth and fifth embodiments, the number of rotations of the input shaft TR2a of the transmission unit TR2 and the number of rotations of the output shaft DG2a of the differential gear DG2 and the relay shaft 143C are different. The rotational speed of the torque applying motor 131 (FIG. 15) is controlled so as to compensate for the difference in the numbers.

(Seventh embodiment)
FIG. 19 is an external view of a rotary torsion testing device 100B according to the seventh embodiment of the present invention. As shown in FIG. 19, a torsion testing device 100B according to this embodiment performs a rotational torsion test on a differential gear DG1.

Since the torsion testing apparatus 100B of the present embodiment has two systems (DG1a, DG1b) of output shafts of the differential gear DG1, second gearboxes (142B1, 142B2) for returning the output of the differential gear DG1 to the first gearbox 141B ), bevel gear boxes (144B1, 144B2) and relay shafts (143B1, 143B2) are provided in two systems each. Specifically, the output shafts DG1a and DG1b of the differential gear DG1 are connected to relay shafts 143B1 and 143B2 via second gearboxes 142B1 and 142B2 and bevel gearboxes 144B1 and 144B2, respectively.

The first gear box 141B also includes a gear 141Bb and gears 141Ba and 141Bc that engage with the gear 141Bb. A tubular portion of a casing of the torque applying unit 130 is connected to the gear 141Bb. Relay shafts 143B1 and 143B2 are connected to the gears 141Ba and 141Bc, respectively. Accordingly, when the inverter motor 80 is driven, the relay shafts 143B1 and 143B2 and the casing 131 of the torque applying unit 130 rotate.

The output shafts DG1a, DG1b and the input shaft DG1c of the differential gear DG1 are connected to the shafts of the gear boxes 142B1, 142B2 and the torque applying unit 130 via torque sensors 172a, 172b and 172c, respectively. Torque sensors 172a, 172b, and 172c each have a shaft 1170 with a strain gauge 1174 attached to a constricted portion 1172 shown in FIG. 13 (second embodiment). directly to).

In the present embodiment, since the rotation speed of the input shaft DG1c of the differential gear DG1 and the rotation speed of the output shafts DG1a and DG1b are different, the servo motor unit incorporated in the torque applying unit 130 compensates for this difference in rotation speed. 150 rpm are controlled.

(Eighth embodiment)
Also, the present invention can be applied to a test apparatus for power transmission devices for FF vehicles. A torsion testing apparatus according to an eighth embodiment of the present invention, which will be described below, is a power circulation type testing apparatus that performs a rotational torsion test on the power transmission system of an FF vehicle.

FIG. 20 is an external view of a torsion testing device 100C according to the eighth embodiment of the present invention. As shown in FIG. 20, the torsion test device 100C of the present embodiment performs a rotational torsion test on a transmission unit TR for an FF vehicle.

As shown in FIG. 20, the input shaft TRa and the output shafts TRb, TRc of the transmission unit TR are connected to the first gear box 141C via torque sensors 172b, 172b, 172c, respectively, without being decelerated. ing. Also, the input shaft TRa and the output shafts TRb, TRc of the transmission unit TR are arranged substantially parallel to each other. Therefore, in the present embodiment, the input shaft TRa and one output shaft TRb of the transmission unit TR are directly connected to the first gearbox 141C, and the other output shaft TRc is connected to the second gearbox 142C and the output shaft TRc. is connected to the first gear box 141C via a relay shaft 143C arranged substantially parallel to the . That is, the driving force of the output shaft TRc is turned back by 180° by the second gearbox 142C and then transmitted to the first gearbox 141C by the relay shaft 143C.

The first gearbox 141C of this embodiment includes a gear 141Cb and gears 141Ca and 141Cc that engage with the gear 141Cb, respectively. The gear 141Ca is engaged with the gear 141Cb via a pinion gear, and the rotation of the gear 141Cb is decelerated and transmitted to the gear 141Ca. The tubular portion of the casing of the torque applying unit 130 is connected to the gear 141Ca, and the output shaft of the inverter motor 80 is connected to the gear 141Cc via a timing belt. Accordingly, when the inverter motor 80 is driven, the output shaft TRb of the transmission unit TR, the output shaft TRc (via the relay shaft 143C), and the casing of the torque applying unit 130 are rotated.

Further, in the present embodiment, since the transmission unit TR has a reduction ratio, the rotation speed of the input shaft TRa differs from the rotation speed of the output shafts TRb and TRc. Therefore, the rotational speed of the servo motor unit 150 built in the torque applying unit 130 is controlled so as to compensate for this rotational speed difference.

The third to eighth embodiments of the present invention described above are examples in which the present invention is applied to a power circulation type torsion test apparatus using a power transmission system such as a transmission unit as a work. However, the present invention is not limited to the configuration described above. It is also possible to apply the present invention to various tests of tires as in the ninth and tenth embodiments of the present invention described below.

(Ninth embodiment)
FIG. 21 is a top view of a tire wear testing device 100D according to the ninth embodiment of the present invention. The tire wear test device 100D has a power circulation mechanism having the same configuration as that of the third embodiment described above.

The first gearbox 141D has four axial connections 141Da1, 141Da2, 141Db1 and 141Db2. Also, the second gearbox 142D has two axial connection portions 142Da and 142Db.

In this embodiment, both ends of the shaft 145, which is the rotation shaft of the rotary drum DR as the simulated road surface, are connected to the shaft connection portion 141Da2 of the first gear box 141D and the shaft connection portion 142Da of the second gear box 142D, respectively. ing. Both ends of the shaft 144, which is the rotating shaft of the tire T to be tested, are connected to the shaft connecting portion 141Db2 of the first gear box 141D and the shaft connecting portion 142Db of the second gear box 142D, respectively.

As in the second embodiment, the output shaft 121a of the workpiece rotating servomotor 121 for driving the tire T and the rotating drum DR is rotated by a belt mechanism composed of a driving pulley 122, a driven pulley 123 and an endless belt 124. The shaft 123a of the driven pulley 123 is rotationally driven through the shaft 123a. The shaft 123a is connected to the shaft connecting portion 141a of the first gearbox 141D.

The tubular portion 131a of the casing 131 of the torque applying unit 130 is connected to the axial connection portion 141Db1 of the first gearbox 141D. Also, the output shaft 133b of the speed reducer 133 of the torque applying unit 130 is connected to one end of the tire T shaft 144 via a coupling 151D arranged inside the first gear box 141D.

One end of the shaft 145 for the rotary drum DR attached to the first gearbox 141D is connected to the shaft 123a of the driven pulley 123 via a coupling 153D arranged inside the first gearbox 141D. ing.

The shaft 123a attached to the shaft connection portion 141Da1 of the first gearbox 141D and the shaft (tubular portion 131a) attached to the shaft connection portion 141Db1 are connected to different gears provided inside the first gearbox 141, respectively. It has become so. These gears are meshed with each other inside the second gear box 142, and when the work rotation servomotor 121 is driven, the shaft 145 for the rotary drum DR and the casing 131 of the torque applying unit 130 are rotated. ing.

The shaft 145 attached to the shaft connection portion 142Da of the second gear box 142 and the shaft 144 attached to the shaft connection portion 142Db are connected to different gears provided inside the second gear box 142, respectively. It has become. These gears mesh with each other inside the second gear box 142 , and the rotation of the shaft 144 is transmitted to the shaft 145 by the second gear box 142 .

With the configuration as described above, by driving the rotation servomotor 121, it is possible to rotate the rotary drum DR and the tire T while circulating the power. As shown in FIG. 21, since the diameters of the rotating drum DR and the tire T are different in the present embodiment, the gear ratio in the first gear box 141D and the second gear box 142D is the same as that of the rotating drum DR and the tire T. It is set to a value according to the ratio of the diameters of

In the tire wear test apparatus configured as described above, by setting the tire T on the shaft 144 and driving the rotation servomotor 121, the tire T and the rotary drum DR are rotated. In this state, the torque-applying servomotor unit 131 (FIG. 2) of the torque-applying unit 130 is driven to apply torque in the forward and reverse directions to the tire T, thereby simulating wear during acceleration and deceleration of the automobile. It becomes possible to conduct a test.

(Tenth embodiment)
Another example in which the present invention is applied to tire testing will be introduced. A tire testing device according to a tenth embodiment of the present invention, which will be described below, is a testing device that performs wear tests, endurance tests, running stability tests, and the like of tires.

22 and 23 are perspective views of the tire testing device 100D according to the tenth embodiment of the present invention, viewed from different directions. The tire testing apparatus 100D of this embodiment includes a rotating drum 10 having a simulated road surface formed on its outer peripheral surface, an inverter motor 80 for rotating the casing of the rotating drum 10 and the torque applying unit 130, an alignment control mechanism 160, and an alignment control mechanism 160. A torque application unit 130 that applies torque to the tire T that is rotatably supported by the control mechanism 160 is provided. The torque applying unit 130 incorporates a servo motor unit 150 having the same configuration as that of the first embodiment.

The rotating drum 10 is rotatably supported by a pair of bearings 11a. A pulley 12 a is attached to the output shaft of the inverter motor 80 , and a pulley 12 b is attached to one shaft of the rotating drum 10 . The pulley 12a and the pulley 12b are connected by a drive belt. A pulley 12 c is attached to the other shaft of the rotating drum 10 via a relay shaft 13 . The relay shaft 13 is rotatably supported by a bearing 11b near one end to which a pulley is attached. Pulley 12c is connected to pulley 12d by a drive belt. The pulley 12d is coaxially fixed to the pulley 12e and rotatably supported together with the pulley 12e by a bearing 11c (FIG. 27). The pulley 12e is also connected to the tubular portion of the casing of the torquing unit 130 by a drive belt.

Also, the drive shaft of the servo motor unit 150 built in the torque applying unit 130 is connected to the wheel of the alignment control mechanism 160 on which the tire T is mounted via the intermediate shaft 14 and flexible coupling.

Accordingly, when the inverter motor 80 is driven, the rotating drum 10 rotates, and the casing of the torque applying unit 130 connected to the inverter motor 80 via the rotating drum 10 rotates. Further, the rotating drum 10 and the tire T rotate in opposite directions so that the peripheral speed at the contact portion is the same when the torque applying unit 130 is not operated. Further, dynamic driving force and braking force can be applied to the tire T by operating the torque applying unit 130 .

The alignment control mechanism 160 of the present embodiment supports the tire T, which is a test piece, mounted on the wheel, presses the tread portion against the simulated road surface of the rotating drum 10, and aligns the tire T with respect to the simulated road surface. It is a mechanism that adjusts the load (ground pressure) to the set state. The alignment control mechanism 160 includes a tire load adjustment unit 161 that moves the position of the rotation axis of the tire T in the radial direction of the rotary drum 10 to adjust the tire load, and a tire load adjustment unit 161 that tilts the rotation axis of the tire T around the perpendicular to the simulated road surface. A slip angle adjustment unit 162 that adjusts the slip angle of the tire T with respect to the simulated road surface, a camber angle adjustment unit 163 that adjusts the camber angle by tilting the rotation axis of the tire T with respect to the rotation axis of the rotating drum 10, and the tire A traverse device 164 is provided to move T in the direction of the rotation axis.

By setting the tire T in the tire testing apparatus 100D configured as described above and driving the inverter motor 80 for rotational driving, the tire T and the rotating drum 10 rotate at the same peripheral speed. In this state, the servo motor unit 150 of the torque applying unit 130 is driven to apply a driving force and a braking force to the tire T, thereby simulating an actual running condition for a tire wear test, an endurance test, and a running stability test. It becomes possible to conduct tests and the like.

(Eleventh embodiment)
Next, a test apparatus for a power absorption type power transmission device using a power simulator according to an embodiment of the present invention will be described.

FIG. 24 is an external view of a power absorption type endurance test device 100F for FR transmissions according to the eleventh embodiment of the present invention.

The test apparatus 100F includes a power simulator 100X including an inverter motor 80 and a load applying section 100 containing a servomotor unit 150, a support section S for supporting a case of an FR transmission T as a test piece, and a torque sensor 172a. , 172b and two power-absorbing servomotors 90A and 90B. An input shaft of the FR transmission T is connected to an output shaft of the load applying section 100 via a torque sensor 172a. Also, the output shaft To of the FR transmission T is connected to the pulley portion 180 via the torque sensor 172b. The torque sensors 172a, 172b have the same configuration as the torque sensors 172a, 172b, 172c of the seventh embodiment.

The pulley unit 180 is connected to two power absorbing servomotors 90A and 90B by two drive belts. The two power-absorbing servomotors 90A and 90B are synchronously driven to apply a load to the output shaft To of the FR transmission T. As shown in FIG.

(12th embodiment)
FIG. 25 is an external view of a power absorption type endurance test apparatus 100G for FF transmissions according to the twelfth embodiment of the present invention.

An FF transmission TR, which is a specimen, has one input shaft and two output shafts TRb and TRc. An input shaft of the FF transmission TR is connected to an output shaft of the load applying section 100 via the torque sensor 172a. Also, the output shaft TRb (TRc) of the FF transmission TR is connected to the power absorbing servomotor 90B (90C) via the torque sensor 172b (172c), the pulley portion 180b (180c), and the drive belt. The power absorbing servomotor 90B (90C) applies a load to the output shaft TRb (TRc) of the FF transmission TR. The torque sensors 172a, 172b, 172c have the same configuration as the torque sensors 172a, 172b, 172c of the seventh embodiment.

(13th embodiment)
Next, a low-speed rotary torsion testing apparatus according to a thirteenth embodiment of the present invention will be described. FIG. 26 is a side view of a torsion testing device 3100 according to the thirteenth embodiment of the invention. A torsion test device 3100 of this embodiment is a device for performing a rotational torsion test on a specimen T1 (for example, a transmission unit for an FR vehicle) having two rotation shafts. That is, the torsion test apparatus 3100 rotates the two rotating shafts of the test piece T1 while synchronously rotating the two rotating shafts and giving a phase difference to the rotation of the two rotating shafts while applying torque. Let The torsion testing apparatus 3100 of this embodiment includes a control unit C3 that integrally controls the operations of the first driving section 3110, the second driving section 3120, and the torsion testing apparatus 3100. FIG.

First, the structure of the first driving section 3110 will be described. FIG. 27 is a partially cutaway side view of the first driving section 3110. FIG. The first driving section 3110 includes a main body 3110a and a base 3110b that supports the main body 3110a at a predetermined height. The main body 3110a includes a servo motor unit 150, a speed reducer 3113, a case 3114, a spindle 3115, a chuck device 3116, a torque sensor 3117, a slip ring 3119a and a brush 3119b, and the main body 3110a is arranged horizontally on the top of the base 3110b. It is assembled on the movable plate 3111 which is mounted. A servo motor unit 150 is the same as in the first embodiment. The servo motor unit 150 is fixed on the movable plate 3111 with its output shaft (not shown) directed horizontally. Also, the movable plate 3111 of the base 3110b is provided slidably in the direction of the output shaft of the servo motor unit 150 (horizontal direction in FIG. 26).

An output shaft (not shown) of the servo motor unit 150 is connected to an input shaft (not shown) of the speed reducer 3113 by a coupling (not shown). An output shaft 3113 a of the speed reducer 3113 is connected to one end of the torque sensor 3117 . The other end of torque sensor 3117 is connected to one end of spindle 3115 . The spindle 3115 is rotatably supported by a bearing 3114a fixed to the frame 3114b of the case 3114. As shown in FIG. A chuck device 3116 is fixed to the other end of the spindle 3115 for attaching one end (one of the rotating shafts) of the test piece T1 to the first drive section 3110 . When the servomotor unit 150 is driven, the rotational motion of the output shaft of the servomotor unit 150 is decelerated by the speed reducer 113, and passed through the torque sensor 3117, spindle 3115 and chuck device 3116 to one end of the test piece T1. It is designed to be transmitted. A rotary encoder (not shown) that detects the rotation angle of the spindle 3115 is attached to the spindle 3115 .

As shown in FIG. 27, the speed reducer 3113 is fixed to the frame 3114b of the case 3114. As shown in FIG. The speed reducer 3113 also includes a gear case and a gear mechanism rotatably supported by the gear case via bearings (not shown). That is, the case 3114 covers the power transmission shaft from the speed reducer 3113 to the chuck device 3116 and also functions as a device frame that rotatably supports the power transmission shaft at the position of the speed reducer 3113 and the spindle 3115 . That is, the gear mechanism of the speed reducer 3113 to which one end of the torque sensor 3117 is connected and the spindle 3115 to which the other end of the torque sensor 3117 is connected are both rotatable on the frame 3114b of the case 3114 via bearings. Supported. Therefore, the torque sensor 3117 is not subjected to a bending moment due to the weight of the gear mechanism of the speed reducer 3113 or the spindle 3115 (and the chuck device 3116), and only the test load (torsion load) is applied. Therefore, the test load is detected with high accuracy. can do.

A plurality of slip rings 3119a are formed on the cylindrical surface of the torque sensor 3117 on one end side. On the other hand, a brush holding frame 3119c is fixed to the movable plate 3111 so as to surround the slip ring 3119a from the outer peripheral side. A plurality of brushes 3119b are attached to the inner periphery of the brush holding frame 3119c, each contacting with a corresponding slip ring 3119a. When the servo motor unit 150 is driven and the torque sensor 3117 is rotating, the brush 3119b slips on the slip ring 3119a while maintaining contact with the slip ring 3119a. The output signal of the torque sensor 3117 is configured to be output to a slip ring 3119a so that the output signal of the torque sensor 3117 can be taken out of the first driving section 3110 via a brush 3119b that contacts the slip ring 3119a. It's becoming

The second driving section 3120 (FIG. 26) has the same structure as the first driving section 3110, and when the servo motor unit 150 is driven, the chuck device 3126 rotates. The other end (one of the rotating shafts) of the specimen T1 is fixed to the chuck device 3126 . The housing of the specimen T1 is fixed to the support frame S.

A torsion testing apparatus 3100 of this embodiment is configured to hold an output shaft O and an input shaft I (engine side) of a test piece T1, which is a transmission unit for an FR vehicle, through chuck devices of a first drive section 3110 and a second drive section 3120, respectively. 3116 and 3126, the servomotor units 150 and 150 synchronously rotate and drive the two chuck devices 3116 and 3126, and the rotational speed (or phase of rotation) of the two chuck devices 3116 and 3126 are made different to rotate the specimen T1. It applies a torsional load. For example, the chuck device 3126 of the second drive unit 3120 is driven to rotate at a constant speed, and the chuck device 3116 is rotationally driven so that the torque detected by the torque sensor 3117 of the first drive unit 3110 fluctuates according to a predetermined waveform, A periodically fluctuating torque is applied to the test piece T1, which is a transmission unit.

Thus, the torsion testing apparatus 3100 of the present embodiment can precisely drive both the input shaft I and the output shaft O of the transmission unit by the servo motor units 150, 150, so that the transmission unit can be rotationally driven. By applying fluctuating torque to each shaft of the transmission unit while rotating, the test can be performed under conditions close to the actual driving conditions of the automobile.

When performing a rotational torsion test on a device such as a transmission unit in which the input shaft I and the output shaft O are connected via a gear or the like, the magnitudes of the torques applied to the input shaft I and the output shaft O do not necessarily match. Therefore, in order to more accurately grasp the behavior of the test piece T1 during the torsion test, it is preferable to measure the torque on the input shaft I side and the output shaft O side separately. In this embodiment, as described above, both the first drive section 3110 and the second drive section 3120 are provided with torque sensors, so that the input shaft I side and the output shaft O side of the transmission unit (specimen T1) and torque can be measured separately.

In the above example, the input shaft I side of the transmission unit is rotationally driven at a constant speed and the output shaft O side is configured to apply torque, but the present invention is not limited to the above example. That is, the configuration may be such that the output shaft O side of the transmission unit is driven to rotate at a constant speed, and fluctuating torque is applied to the input shaft I side. Alternatively, both the input shaft I side and the output shaft O side of the transmission unit may be rotationally driven at varying rotational speeds. Moreover, it is also possible to adopt a configuration in which only the torque of each shaft is controlled without controlling the number of rotations. Alternatively, the torque or the number of revolutions may be varied according to a predetermined waveform. Torque and rotation speed can be varied according to arbitrary waveforms generated by, for example, a function generator. Further, it is also possible to control the torque and rotation speed of each shaft of the specimen T1 based on waveform data of torque and rotation speed measured in an actual running test.

The torsion testing apparatus 3100 of this embodiment can adjust the distance between the chuck devices 3116 and 3126 so as to be compatible with transmission units of various sizes. Specifically, a movable plate driving mechanism (not shown) enables the movable plate 3111 of the first driving section 3110 to move relative to the base 3110b in the rotation axis direction (horizontal direction in FIG. 26) of the chuck device 3116. ing. During the rotational torsion test, the movable plate 3111 is firmly fixed to the base 3110b by a lock mechanism (not shown). The second driving section 3120 also has a movable plate driving mechanism similar to that of the first driving section 3110 .

The torsion testing apparatus 3100 according to the thirteenth embodiment of the present invention described above performs a rotational torsion test on transmission units for FR vehicles. Apparatus for performing rotational torsion testing of other power transmission mechanisms is also included in the present invention, without being limited in configuration. The first, second, and third modifications of the thirteenth embodiment of the present invention described below are torsion tests suitable for testing transmission units for FF vehicles, differential gear units, and transmission units for 4WD vehicles, respectively. It is a configuration example of an apparatus.

(First modification of the thirteenth embodiment)
FIG. 28 is a plan view of a torsion testing device 3200 according to the first modification of the thirteenth embodiment of the present invention. As described above, this modification is a configuration example of a torsion testing apparatus suitable for a rotational torsion test using a transmission unit for an FF vehicle as the specimen T2. The specimen T2 is a transmission unit incorporating a differential gear, and has an input shaft I, a left output shaft OL and a right output shaft OR.

The torsion test apparatus 3200 of this modified example includes a first drive section 3210 that drives the input shaft I of the test piece T2, a second drive section 3220 that drives the left output shaft OL, and a third drive section that drives the right output shaft OR. 3230 is provided. The torsion tester 3200 also includes a control unit C3a that integrally controls its operation. The structures of the first driving section 3210, the second driving section 3220 and the third driving section 3230 are the same as those of the first driving section 3110 and the second driving section 3120 according to the basic example of the thirteenth embodiment. Therefore, redundant description of specific configurations is omitted.

When performing a rotational torsion test of the specimen T2 using the torsion testing apparatus 3200 of this modification, for example, the input shaft I is driven at a predetermined number of rotations by the first driving section 3210, and at the same time, the second driving section 3220 and The third drive unit 3230 rotationally drives the left output shaft OL and the right output shaft OR so as to apply a predetermined torque.

By controlling the first drive section 3210, the second drive section 3220, and the third drive section 3230 as described above, the transmission unit is rotationally driven while applying fluctuating torque to each shaft of the transmission unit. Tests can be conducted under conditions close to actual driving conditions.

Further, the transmission unit to be tested using the torsion testing device 3200 of this modified example is a device in which the input shaft I, the left output shaft OL, and the right output shaft OR are connected via gears or the like. When conducting a test, the magnitudes of the torques applied to the input shaft I, the left output shaft OL, and the right output shaft OR do not match. Also, the torques applied to the left output shaft OL and the right output shaft OR do not necessarily match. Therefore, in order to more accurately grasp the behavior of the specimen T2 during the torsion test, it is preferable to measure the torque applied to the input shaft I, the left output shaft OL, and the right output shaft OR individually. In this modification, since torque sensors are provided in all of the first drive section 3210, the second drive section 3220, and the third drive section 3230, the input shaft I and the left output shaft of the transmission unit (specimen T2) The torque applied to each of the OL and the right output shaft OR can be measured separately.

The second driving section 3220 and the third driving section 3230 may be controlled so that the torque of the left output shaft OL and the torque of the right output shaft OR draw the same waveform, or the two may be different ( For example, the first driving section 3210, the second driving section 3220, and the third driving section 3230 may be controlled so as to draw waveforms of opposite phases.

Alternatively, the left output shaft OL and the right output shaft OR may be rotationally driven at a constant speed, and the input shaft I may be driven such that the speed varies in a constant cycle. Alternatively, all of the input shaft I, the left output shaft OL, and the right output shaft OR may be driven so that the rotational speeds thereof vary individually.

(Second modification of the thirteenth embodiment)
Next, a second modification of the thirteenth embodiment of the present invention will be described. FIG. 19 is a plan view of a torsion testing device 3300 according to this modification. This modified example is a configuration example of a torsion testing apparatus suitable for a rotational torsion test using a differential gear unit for an FR vehicle as a specimen T3. As in the first modification, the test piece T3 has an input shaft I, a left output shaft OL and a right output shaft OR.

The torsion test apparatus 3300 of this modified example includes a first drive section 3310 that drives the input shaft I of the test piece T3, a second drive section 3320 that drives the left output shaft OL, and a third drive section that drives the right output shaft OR. 3330 is provided. The torsion tester 3300 also has a control unit C3b that integrally controls its operation. The structures of the first driving section 3310, the second driving section 3320, and the third driving section 3330 are the same as the first driving section 3110 and the second driving section 3120 according to the basic example of the thirteenth embodiment. Description of the specific configuration is omitted.

When the torsion test apparatus 3300 of this modified example performs a rotational torsion test on the specimen T3, for example, the input shaft I is driven at a predetermined number of rotations by the first driving section 3310, and simultaneously, the second driving section 320 and the third Drive unit 3330 drives so that torque is applied to left output shaft OL and right output shaft OR.

By controlling the first drive section 3310, the second drive section 3320 and the third drive section 3330 as described above, the torque is applied to each axis of the test piece T3 while rotating each axis of the test piece T3. This makes it possible to conduct tests under conditions close to actual usage conditions.

Similar to the transmission unit, the differential gear unit is also a device in which the input shaft I, the left output shaft OL and the right output shaft OR are connected via gears. and the magnitude of the torque applied to the left output shaft OL and the right output shaft OR do not match. Also, the magnitude of the torque applied to the left output shaft OL and the right output shaft OR are not always the same. Therefore, in order to more accurately grasp the behavior of the test piece T3 during testing, it is desirable to measure the torques of the input shaft I, the left output shaft OL, and the right output shaft OR individually. In this modification, since torque sensors are provided in all of the first driving section 3310, the second driving section 3320, and the third driving section 3330, the input shaft I of the differential gear unit (specimen T3) and the left output The torque applied to each of the shaft OL and the right output shaft OR can be measured separately.

The second drive unit 3320 and the third drive unit 3330 may be controlled so that the rotation speed of the input shaft I and the rotation speeds of the left output shaft OL and the right output shaft OR draw the same waveform. Further, the second drive section 3320 and the third drive section 3330 may be controlled so that they draw different waveforms (for example, the speed difference with the input shaft I is in opposite phase).

Alternatively, the left output shaft OL and the right output shaft OR may be driven to rotate at a constant speed, and the input shaft I may be driven such that the speed fluctuates at a constant cycle. Alternatively, all of the input shaft I, the left output shaft OL and the right output shaft OR may be configured to be driven such that the rotation speed varies.

(Third modification of the thirteenth embodiment)
FIG. 20 is a plan view of a torsion testing device 3400 according to a third modified example of the thirteenth embodiment of the present invention. A torsion testing apparatus 3400 of this modification is a configuration example of a torsion testing apparatus suitable for a rotational torsion test of a specimen T4 having four rotation axes. As an example, a case where a 4WD system is tested as a test piece T4 will be described below. The test sample T4 is an FF-based electronically controlled 4WD system equipped with a transmission, a front differential gear, a transfer, and an electronically controlled multi-plate clutch (not shown). The test piece T4 is connected to an input shaft I connected to an engine, a left output shaft OL and a right output shaft OR connected to drive shafts for the left and right front wheels, and a propeller shaft that transmits power to the rear wheels. It has a rear output shaft OP. The driving force input from the input shaft I to the test piece T4 is decelerated by the transmission provided on the test piece T4, and then distributed to the left output shaft OL and the right output shaft OR via the front differential gear. A portion of the driving force transmitted to the front differential gear is branched by a transfer and output from the rear output shaft OP.

The torsion test apparatus 3400 of this modified example includes a first drive section 3410 that drives the input shaft I of the test piece T4, a second drive section 3420 that drives the left output shaft OL, and a third drive section that drives the right output shaft OR. 3430 and a fourth drive section 3440 for driving the rear output shaft OP. The torsion tester 3400 also has a control unit C3c that integrally controls its operation. The structures of the first driving section 3410, the second driving section 3420, the third driving section 3430 and the fourth driving section 3440 are all the same as the first driving section 3110 and the second driving section 3120 of the basic example of the thirteenth embodiment. Therefore, redundant description of specific configurations is omitted.

(14th embodiment)
In the first to thirteenth embodiments described above, the two-axis output servomotor 150A according to the embodiment of the present invention is used in connection with the servomotor 150B having one output shaft. As in the fourteenth embodiment of the invention, the two-axis output servomotor 150B can also be used alone.

FIG. 31 is a side view of a torsion testing device 4000 according to the fourteenth embodiment of the invention. The torsion test device 4000 is a device that uses only one 2-axis output servomotor 150A to enable simultaneous rotational torsion testing of two specimens T3a and T3b. The torsion test device 4000 includes a fixed base 4100, a drive section 4200, a first reaction section 4400A, a second reaction section 4400B, and a control unit C4.

FIG. 32 is an enlarged view of the driving section 4200. FIG. The drive unit 4200 includes a two-axis output servomotor 150A and a pair of drive transmission units 4200A and 4200B. The two-axis output servomotor 150A is connected to the control unit C4, and its drive is controlled by the control unit C4. The drive transmission units 4200A and 4200B decelerate the rotation of the first output shaft 150A2a and the second output shaft 150A2b of the biaxial output servomotor 150A, respectively, and transmit them to the input shafts of the specimens T3a and T3b. Since the drive transmission section 4200A and the drive transmission section 4200B have the same configuration, only one drive transmission section 4200A will be described in detail.

The drive transmission section 4200A includes a frame 4210, a reduction gear 4220, a pulley 4230, a timing belt 4240, a rotary encoder 4250, and a chuck device 4260. The frame 4210 is an angle (L-shaped material) frame mounted on the fixed base 4100, and includes a bottom plate 4212 which is a flat plate horizontally arranged on the fixed base 4100 and a flat plate erected from one end of the upper surface of the bottom plate 4212. and a pair of rib plates 4216 vertically connected to the bottom plate 4212 and the vertical plate 4214 . The bottom plate 4212, vertical plate 4214 and rib plate 4216 are connected to each other by welding. The vertical plate 4214 is arranged perpendicular to the first output shaft 150A2a of the biaxial output servomotor 150A, and has an opening 4214a formed coaxially with the first output shaft 150A2a. A reduction gear 4220 is inserted and fixed in an opening 4214 a of the vertical plate 4214 .

A first bracket 150A3 of the biaxial output servomotor 150A is attached to the input side flange plate 4224 of the speed reducer 4220 with bolts. The first bracket 150A3 is fixed to the input side flange plate 4224 via the reinforcing plate 4212 not only by the mounting seat surface (the right side surface in FIG. 31) but also by the tapped holes 150A3t provided on the lower surface thereof. As a result, the input side flange plate 4224 of the speed reducer 4220 and the first bracket 150A3 of the two-axis output servomotor 150A are connected with high rigidity, enabling highly accurate testing.

A first output shaft 150A2a of the two-axis output servomotor 150A is connected to an input shaft (not shown) of the speed reducer 4220. As shown in FIG. A chuck device 4260 is attached to the tip of the output shaft 4228 of the speed reducer 4220 . An input shaft of the specimen T3a is attached to the chuck device 4260 . The rotation of the first output shaft 150A2a of the two-axis output servomotor 150A is decelerated by the speed reducer 4220, and after the torque is amplified, it is transmitted to the input shaft of the specimen T3a via the chuck device 4260.

A lubricating cup 4222 is provided in the speed reducer 4220, and the internal space of the speed reducer 4220 is filled with lubricating oil so that each gear constituting the speed reducer 4220 is always completely immersed in the lubricating oil. there is In the torsion test, a reciprocating torsional load in the normal range is applied to the test piece, so the twisting angle of the test piece is several tens of degrees at most, and the amplitude of the repeated rotation of the input shaft of the reduction gear is one rotation (360°). It is often missing. By filling the internal space of the speed reducer 4220 with lubricating oil, even in such a usage pattern, the oil film of the gear mechanism constituting the speed reducer can be prevented from running out, and the heat dissipation effect of the lubricating oil can be enhanced. Burn-in is effectively prevented.

A pulley 4230 is provided on the outer circumference of the output shaft 4228 . A rotary encoder 4250 is arranged on the vertical plate 4214 of the frame 4210 below the speed reducer 4220 . A timing belt 4240 is wound around a pulley 4252 attached to the input shaft of the rotary encoder 4250 and a pulley 4230 attached to the output shaft 4228 of the reduction gear 4220, and the rotation of the output shaft 4228 of the reduction gear 4220 is It is transmitted to and detected by a rotary encoder 4250 via a timing belt 4240 . The rotary encoder 4250 is connected to the control unit C4, and a signal indicating the rotation detected by the rotary encoder 4250 is sent to the control unit C4.

Next, the first reaction force portion 4400A will be described. Note that the second reaction force portion 4400B has the same configuration as the first reaction force portion 4400A, so a detailed description thereof will be omitted.

The first reaction force part 4400A includes a frame 4410, a torque sensor 4420, a spindle 4440, a bearing part 4460 and a chuck device 4480. The frame 4410 is an angle (L-shaped material) frame attached to the fixed base 4100 with bolts B, and includes a bottom plate portion 4412 horizontally arranged on the fixed base 4100 and one end of the top surface of the bottom plate portion 4412 (Fig. 31), and a pair of rib plates 2416 vertically connected to the bottom plate portion 4412 and the vertical plate 2414. As shown in FIG. The bottom plate portion 4412, vertical plate 4214 and rib plate 4216 are connected to each other by welding. Further, the bearing portion 4460 is fixed with a bolt B on the bottom plate portion 4412 on the driving portion 4200 side of the vertical plate 2414 and the rib plate 2416 .

The fixed base 4100 includes a first reaction portion moving mechanism (not shown) that smoothly moves the first reaction portion 4400A in the direction of the first output shaft 150A2a of the biaxial output servomotor 150A. By activating the first reaction force portion moving mechanism in a state in which the bolt B that fixes the upper portion to the fixed base 4100 is loosened, the first reaction force portion 4400A can be smoothly moved in the direction of the first output shaft 150A2a. ing. The fixed base 4100 also includes a second reaction portion moving mechanism (not shown) that smoothly moves the second reaction portion 4400B in the direction of the second output shaft 150A2b of the biaxial output servomotor 150A.

Torque sensor 4420, spindle 4440, bearing 4460, and chuck device 4480 are arranged coaxially with first output shaft 150A2a of biaxial output servomotor 150A. One end (the left end in FIG. 31) of the torque sensor 4420 is fixed to the vertical plate 4214 of the frame 4410 . One end of a spindle 4440 (the left end in FIG. 31) is fixed to the other end of the torque sensor 4420, and a chuck device 4480 is attached to the other end of the spindle 4440. The output shaft of the test piece T3a is attached to the chuck device 4480 .

The torque of the output shaft of the test piece T3a is transmitted to the torque sensor 4420 via the chuck device 4480 and the spindle 4440 and detected. The torque sensor 4420 is connected to the control unit C4, and the signal indicating the torque of the output shaft of the test piece T3a detected by the torque sensor 4420 is sent to the control unit C4 and processed.

The spindle 4440 is rotatably supported by a bearing 4460 in the vicinity of the other end (the end on the chuck device 4480 side). Therefore, since the torque sensor 4420 and the spindle 4440 are both supported by the vertical plate 2414 and the bearing portion 4460, an increase in the detection error of the torque sensor 4420 due to a large bending moment being applied to the torque sensor 4420 is prevented. be.

When a rotational torsion test is performed using the torsion test apparatus 4000 having the above configuration, the input shaft of the test piece T3a is attached to the chuck device 4260 of the drive transmission section 4200A, and the chuck device of the first reaction force section 4400A is attached. 4480 is attached to the output shaft of the test piece T3a. Similarly, the input shaft of the test piece T3b is attached to the chuck device 4260 of the drive transmission section 4200B, and the output shaft of the test piece T3b is attached to the chuck device 4480 of the second reaction force section 4400B. When the two-axis output servomotor 150A is driven in this state, the first output shaft 150A2a and the second output shaft 150A2b rotate in the same phase, and the chuck devices 4260 of the drive transmission units 4200A and 4200B also rotate in the same phase. . As a result, the same amount of torsion is applied to the test pieces T3a and T3b, that is, the test pieces T3a and T3b are subjected to the torsion test under the same conditions.

According to the configuration of the fourteenth embodiment described above, it is possible to simultaneously perform torsion tests (fatigue tests) on two specimens T3a and T3b using one servomotor and control unit C4. test can be performed.

In addition, instead of the drive transmission units 4200A and 4200B, for example, by providing a linear motion converter such as a feed screw mechanism, the two specimens T3a and T3b are repeatedly applied with a compressive force and a tensile force (or alternatively, the specimens T3a, T3b, A tension/compression test apparatus is obtained in which one side of T3b is in compression and the other side is in tension). With this configuration, it is possible to simultaneously perform a cyclic stretching test (or a tensile test on the test piece T3a and a compression test on the test piece T3b) on the two test pieces T3a and T3b. Also, at this time, by eliminating the first reaction force part 4400A and the second reaction force part 4400B, it becomes possible to perform the vibration test of the two specimens T3a and T3b at the same time.

(15th embodiment)
The two-axis output servomotor 150A and the servomotor unit 150 according to the embodiment of the present invention can also be used as a drive source for a linear motion actuator in combination with a linear motion converter such as a feed screw mechanism. Using such a linear actuator, for example, a vibration testing device or a tension/compression testing device can be realized.

FIG. 33 is a top view of a vibration test device (vibrating device) 5000 according to the fifteenth embodiment of the present invention. In the vibration test apparatus 5000 of this embodiment, a workpiece to be subjected to a vibration test is fixed on a table 5100, and first, second and third actuators 5200, 5300 and 5400 are used to move the table 5100 and the workpiece thereon. are excited in three orthogonal axial directions. In the following description, the direction in which the first actuator 5200 vibrates the table 5100 (vertical direction in FIG. 33) is the X-axis direction, and the direction in which the second actuator 5300 vibrates the table 5100 (horizontal direction in FIG. 33). ) is defined as the Y-axis direction, and the direction in which the third actuator 5400 vibrates the table, that is, the vertical direction (in FIG. 33, the direction perpendicular to the paper surface) is defined as the Z-axis direction.

FIG. 38 is a block diagram of a control system for a vibration test apparatus according to an embodiment of the invention. The first, second and third actuators 5200, 5300 and 5400 are provided with vibration sensors 5220, 5320 and 5420, respectively. Based on the outputs of these vibration sensors, the control unit C5 feedback-controls the first, second and third actuators 5200, 5300 and 5400 (specifically, the servo motor units 150X, 150Y and 150Z) to achieve desired vibrations. of amplitude and frequency (these parameters are typically set as a function of time). The servo motor units 150X, 150Y, 150Z are the same as the servo motor unit 150 of the first embodiment.

The first, second and third actuators 5200, 5300 and 5400 are configured such that motors, power transmission members and the like are mounted on base plates 5202, 5302 and 5402, respectively. The base plates 5202, 5302, 5402 are fixed on the device base 5002 by bolts (not shown).

Also, adjusters A are arranged on the device base 5002 at a plurality of positions close to the base plates 5202 , 5302 , 5402 . The adjuster A has a female threaded portion A1 fixed to the device base 5002 with a bolt AB, and a male threaded portion A2 screwed into the female threaded portion A1. The male threaded portion A2 is a cylindrical member having a screw thread formed on its cylindrical surface. The portion A2 can be advanced and retracted with respect to the corresponding base plate. One end of the male threaded portion A2 (proximal side with respect to the corresponding base plate) is formed in a substantially spherical shape. Fine position adjustments can be made. In addition, a hexagonal hole for a hexagonal wrench (not shown) is formed at the other end of the male threaded portion A2 (the side distal to the corresponding base plate). After the base plates 5202, 5302, and 5402 are once fixed, the nut A3 is attached to the male threaded portion A2 so that the male threaded portion A2 will not loosen due to vibrations that may be transmitted from the base plate to the adjuster A during a vibration test. there is The nut A3 is attached so that one end surface thereof abuts against the female threaded portion A1. From this state, the nut A3 is screwed to push in the female threaded portion A1, thereby applying an axial force to the male threaded portion A2 and the female threaded portion A1. Frictional force generated between the threads of the male threaded portion A2 and the female threaded portion A1 by this axial force prevents the female threaded portion A1 from loosening from the male threaded portion A2.

Next, the configuration of first actuator 5200 will be described. FIG. 34 is a side view of the first actuator 5200 according to an embodiment of the present invention viewed from the Y-axis direction (from right to left in FIG. 33). This side view is partially cut away to show the internal structure. FIG. 35 is a top view of the first actuator 5200 with a part cut away to show the internal structure. In the following description, the direction along the X axis from the first actuator 5200 to the table 5100 is the "positive direction of the X axis," and the direction along the X axis from the table 5100 to the first actuator is the "X axis direction." negative direction”.

As shown in FIG. 34, a frame 5222 made up of a plurality of beams 5222a welded together and a top plate 5222b is fixed on the base plate 5202 by welding. Further, the bottom plate 5242 of the support mechanism 5240 for supporting the drive mechanism 5210 for vibrating the table 5100 (FIG. 33) and the connection mechanism 5230 for transmitting the vibration motion of the drive mechanism 5210 to the table 5100 is mounted on the frame. It is fixed on top plate 5222b of 5222 via bolts (not shown).

The drive mechanism 5210 has a servo motor unit 150X, a coupling 5260, a bearing portion 5216, a ball screw 5218 and a ball nut 5219. Coupling 5260 connects drive shaft 152X of servo motor unit 150X and ball screw 5218 . Moreover, the bearing portion 5216 is supported by a bearing support plate 5244 that is vertically welded to the bottom plate 5242 of the support mechanism 5240 and supports the ball screw 5218 so as to be rotatable. Ball nut 5219 engages ball screw 5218 while being supported by bearing support plate 5244 against movement about its axis. Therefore, when the servomotor unit 150X is driven, the ball screw rotates and the ball nut 5219 advances and retreats in its axial direction (that is, the X-axis direction). The motion of the ball nut 5219 is transmitted to the table 5100 via the coupling mechanism 5230, thereby driving the table 5100 in the X-axis direction. By controlling the servo motor unit 150X so as to switch the rotation direction of the servo motor unit 150X in short cycles, the table 5100 can be vibrated in the X-axis direction with desired amplitude and cycle.

A motor support plate 5246 is welded vertically to the top surface of the bottom plate 5242 of the support mechanism 5240 . A servo motor unit 150X is cantilevered on one surface of the motor support plate 5246 (the surface on the negative side of the X axis) so that the drive shaft 152X is perpendicular to the motor support plate 5246. FIG. The motor support plate 5246 is provided with an opening 5246a, and the drive shaft 152X of the servo motor unit 150X passes through this opening 5246a and is connected to the ball screw 5218 on the other side of the motor support plate 5246.

Since the servo motor unit 150X is cantilevered on the motor support plate 5246, a large bending stress is applied to the motor support plate 5246, especially at the welded portion with the bottom plate 5242. FIG. A rib 5248 is provided between the bottom plate 5242 and the motor support plate 5246 to relieve this bending stress.

The bearing portion 5216 has a pair of angular ball bearings 5216a and 5216b (5216a on the negative side of the X-axis and 5216b on the positive side of the X-axis) combined face-to-face. are doing. The angular ball bearings 5216a, 5216b are housed in the hollow portion of the bearing support plate 5244. As shown in FIG. A bearing pressing plate 5216c is provided on one surface of the angular ball bearing 5216b (the surface on the positive side of the X axis). The angular ball bearing 5216b is pushed in the negative direction of the X axis. Further, in the ball screw 5218, a threaded portion 5218a is formed on the cylindrical surface adjacent to the bearing portion 5216 in the negative direction of the X axis. A collar 5217 having an internal thread formed on the inner circumference is attached to the threaded portion 5218 . By rotating the collar 5217 with respect to the ball screw 5218 and moving it in the positive direction of the X-axis, the angular ball bearing 5216a is pushed in the positive direction of the X-axis. In this way, since the angular ball bearings 5216a and 5216b are pushed toward each other, they are in close contact with each other and a suitable preload is applied to the bearings 5216a and 5216b.

Next, the configuration of the connecting portion 5230 will be described. The connecting portion 5230 has a nut guide 5232, a pair of Y-axis rails 5234, a pair of Z-axis rails 5235, an intermediate stage 5231, a pair of X-axis rails 5237, a pair of X-axis runner blocks 5233, and a runner block mounting member 5238. are doing.

Nut guide 5232 is fixed to ball nut 5219 . The pair of Y-axis rails 5234 are rails that both extend in the Y-axis direction, and are fixed to the ends of the nut guides 5232 on the positive X-axis direction side by side in the vertical direction. The pair of Z-axis rails 5235 are rails that both extend in the Z-axis direction, and are fixed to the end of the table 5100 on the negative X-axis direction side by side in the Y-axis direction. The intermediate stage 5231 has a Y-axis runner block 5231a that engages with each of the Y-axis rails 5234 on the surface on the negative side of the X-axis, and a Z-axis runner block 5231b that engages with each of the Z-axis rails 5235 on the X-axis side. It is a block provided on the surface on the positive direction side and configured to be slidable on both the Y-axis rail 5234 and the Z-axis rail 5235 .

That is, the intermediate stage 5231 is slidable in the Z-axis direction with respect to the table 5100 and slidable in the Y-axis direction with respect to the nut guide 5232 . Therefore, the nut guide 5231 can slide in the Y-axis direction and the Z-axis direction with respect to the table 5100 . Therefore, even if the table 5100 is vibrated in the Y-axis direction and/or the Z-axis direction by other actuators 5300 and/or 5400, the nut guide 5232 will not be displaced. That is, bending stress caused by displacement of the table 5100 in the Y-axis direction and/or the Z-axis direction is not applied to the ball screw 5218, the bearing 5216, the coupling 5260, and the like.

The pair of X-axis rails 5237 are rails that both extend in the X-axis direction, and are fixed side by side in the Y-axis direction on the bottom plate 5242 of the support mechanism 5240 . The X-axis runner block 5233 engages with each of the X-axis rails 5237 and is slidable along the X-axis rails 5237 . The runner block mounting member 5238 is a member fixed to the bottom surface of the nut guide 5232 so as to protrude toward both sides in the Y-axis direction, and the X-axis runner block 5233 is fixed to the bottom of the runner block mounting member 5238. In this way, the nut guide 5232 is guided by the X-axis rail 5237 via the runner block mounting member 5238 and the X-axis runner block 5233, thereby being movable only in the X-axis direction.

In this way, since the movement direction of the nut guide 5232 is restricted to the X-axis direction only, when the servo motor unit 150X is driven to rotate the ball screw 5218, the nut guide 5232 and the nut guide 5232 are engaged. The table 5100 moves forward and backward in the X-axis direction.

Position detection means 5250 is arranged on one side surface (front side in FIG. 34, right side in FIG. 35) 5238a of the runner block mounting member 5238 in the Y-axis direction. The position detection means 5250 includes three proximity sensors 5251 arranged at regular intervals in the X-axis direction, a detection plate 5252 provided on the side surface 5238a of the runner block mounting member 5238, and a sensor support plate 5253 supporting the proximity sensors 5251. have. Proximity sensors 5251 are elements capable of detecting whether any object is in proximity (for example, within 1 millimeter) in front of each proximity sensor. Since the side surface 5238a of the runner block mounting member 5238 and the proximity sensors 5251 are sufficiently separated, the proximity sensors 5251 can detect whether or not there is a detection plate 5252 in front of each proximity sensor 5251 . The control unit C5 of the vibration test apparatus 5000 can feedback-control the servo motor unit 150X using, for example, the detection result of the proximity sensor 5251 (FIG. 38).

Further, on the bottom plate 5242 of the support mechanism 5240, regulation blocks 5236 are provided so as to sandwich the X-axis runner blocks 5233 from both sides in the X-axis direction. This regulation block 5236 is for limiting the movement range of the nut guide 5232 . That is, when the servo motor unit 150X is driven to continue moving the nut guide 5232 in the positive direction of the X axis, finally, the restricting block 5236 and the runner block mounting member arranged in the positive direction of the X axis are moved. 5238, and the nut guide 5232 can no longer move in the positive direction of the X axis. The same is true when the nut guide 5232 continues to move in the negative direction of the X axis. 5232 cannot move in the negative direction of the X axis.

The first actuator 5200 and the second actuator 5300 described above have the same structure except that they are installed in different directions (the X-axis and the Y-axis are interchanged). Therefore, detailed description of the second actuator 5300 is omitted.

Next, the configuration of the third actuator 5400 according to the embodiment of the invention will be described. FIG. 36 is a side view of the table 5100 and the third actuator 5400 viewed from the X-axis direction (from the bottom to the top in FIG. 16). This side view is also partly cut away to show the internal structure. Also, FIG. 37 is a side view of the table 5100 and the third actuator 5400 according to the embodiment of the present invention as seen from the Y-axis direction (from left to right in FIG. 33). FIG. 37 is also partially cut away to show the internal structure. In the following description, the direction along the Y-axis from the second actuator 5300 to the table 5100 is the positive Y-axis direction, and the direction along the Y-axis from the table 5100 to the second actuator 5300 is the negative Y-axis direction. Define direction.

As shown in FIGS. 36 and 37, a frame 5422 is provided on the base plate 5402 and includes a plurality of vertically extending beams 5422a and a top plate 5422b arranged to cover the plurality of beams 5422a from above. It is Each beam 5422a has its lower end welded to the upper surface of the base plate 5402 and its upper end welded to the lower surface of the top plate 5422b. Also, the bearing support plate 5442 of the support mechanism 5440 is fixed onto the top plate 5422b of the frame 5422 via bolts (not shown). The bearing support plate 5442 is a member for supporting a drive mechanism 5410 for vibrating the table 5100 (FIG. 33) in the vertical direction, and a coupling mechanism 5430 for transmitting the excitation motion of the drive mechanism 5410 to the table. is.

The drive mechanism 5410 has a servo motor unit 150Z, a coupling 5460, a bearing portion 5416, a ball screw 5418, and a ball nut 5419. The coupling 5460 connects the drive shaft 152Z of the servomotor unit 150Z and the ball screw 5418 together. Moreover, the bearing portion 5416 is fixed to the bearing support plate 5442 described above, and supports the ball screw 5418 rotatably. Ball nut 5419 engages ball screw 5418 while being supported against movement about its axis by bearing support plate 5442 . Therefore, when the servo motor unit 150Z is driven, the ball screw rotates and the ball nut 5419 advances and retreats in its axial direction (that is, Z-axis direction). The motion of the ball nut 5419 is transmitted to the table 5100 via the coupling mechanism 5430, thereby driving the table 5100 in the Z-axis direction. By controlling the servo motor unit 150Z so as to switch the rotation direction of the servo motor unit 150Z in short cycles, the table 5100 can be vibrated in the Z-axis direction (vertical direction) with desired amplitude and cycle.

A motor support plate 5446 extending in the horizontal direction (XY plane) is fixed via two connecting plates 5443 from the lower surface of the bearing support plate 5442 of the support mechanism 5440 . A servo motor unit 150Z is suspended and fixed to the lower surface of the motor support plate 5446 . The motor support plate 5446 is provided with an opening 446a, and the drive shaft 152Z of the servo motor unit 150Z passes through this opening 446a and is connected to the ball screw 5418 on the upper surface side of the motor support plate 5446.

In this embodiment, since the dimension of the servo motor unit 150Z in the axial direction (vertical direction, Z-axis direction) is larger than the height of the frame 5422, most of the servo motor unit 150Z is positioned lower than the base plate 5402. placed in Therefore, the device base 5002 is provided with a hollow portion 5002a for housing the servo motor unit 150Z. Further, the base plate 5402 is provided with an opening 5402a for passing the servo motor unit 150Z.

The bearing portion 5416 is provided so as to pass through the bearing support plate 5442 . The structure of the bearing portion 5416 is the same as that of the bearing portion 5216 (FIGS. 34 and 35) in the first actuator 5200, so detailed description thereof will be omitted.

Next, the configuration of the connecting portion 5430 will be described. The connecting portion 5430 has a movable frame 5432, a pair of X-axis rails 5434, a pair of Y-axis rails 5435, a plurality of intermediate stages 5431, two pairs of Z-axis rails 5437, and two pairs of Z-axis runner blocks 5433. there is

The movable frame 5432 includes a frame portion 5432a fixed to the ball nut 5419, a top plate 5432b fixed to the upper end of the frame portion 5432a, and side walls 5432c fixed to extend downward from both edges of the top plate 5432b in the X-axis direction. have. The pair of Y-axis rails 5435 are rails that both extend in the Y-axis direction, and are fixed to the upper surface of the top plate 5432b of the movable frame 5432 in parallel in the X-axis direction. A pair of X-axis rails 5434 are rails that both extend in the X-axis direction, and are fixed to the lower surface of the table 5100 side by side in the Y-axis direction. The intermediate stage 5431 is a block provided with an upper X-axis runner block 5431a that engages with the X-axis rail 5434 and a lower Y-axis runner block 5431b that engages with each of the Y-axis rails 5435. It is configured to be slidable on both the rail 5434 and the Y-axis rail 435 . One intermediate stage 5431 is provided at each position where the X-axis rail 5434 and the Y-axis rail 5435 intersect. Since two X-axis rails 5434 and two Y-axis rails 5435 are provided, the X-axis rails 5434 and Y-axis rails 5435 intersect at four points. Therefore, four intermediate stages 5431 are used in this embodiment.

Thus, each intermediate stage 5431 is slidable in the X-axis direction with respect to the table 5100 and slidable in the Y-axis direction with respect to the movable frame 5432 . That is, the movable frame 5432 can slide in the X-axis direction and the Y-axis direction with respect to the table 5100 . Therefore, even if the table 5100 is vibrated in the X-axis direction and/or the Y-axis direction by other actuators 5200 and/or 5300, the movable frame 5432 will not be displaced. That is, the bending stress caused by the displacement of the table 5100 in the X-axis direction and/or the Y-axis direction is not applied to the ball screw 5418, the bearing 5416, the coupling 5460, and the like.

In addition, in this embodiment, since the movable frame 5432 supports the relatively heavy table 5100 and workpiece, the distance between the X-axis rail 5434 and the Y-axis rail 5435 is set to the Y-axis rail 5234 of the first actuator 5200 and the Z-axis rail 5435. It is wider than the shaft rail 5235 . Therefore, if the table 5100 and the movable frame 5432 are connected by only one intermediate stage as in the case of the first actuator 5200, the intermediate stage becomes large and the load applied to the movable frame 5432 increases. Therefore, in the present embodiment, a small intermediate stage 5431 is arranged at each intersection of the X-axis rail 5434 and the Y-axis rail 5435 to minimize the load applied to the movable frame 5432. holding back.

The two pairs of Z-axis rails 5437 are rails extending in the Z-axis direction, and are fixed to the side walls 5432c of the movable frame 5432 in pairs in the Y-axis direction. The Z-axis runner block 5433 engages with each of the Z-axis rails 5437 and is slidable along the Z-axis rails 5437 . The Z-axis runner block 5433 is fixed to the upper surface of the top plate 5422b of the frame 5422 via a runner block mounting member 5438. As shown in FIG. The runner block mounting member 5438 has a side plate 5438a arranged substantially parallel to the side wall 5432c of the movable frame 5432, and a bottom plate 5438b fixed to the lower end of the side plate 5438a. It's becoming In addition, in this embodiment, when a work having a high center of gravity and a large weight is fixed on the table 5100, a large moment around the X axis and/or the Y axis is likely to be applied to the movable frame 5432. Therefore, the runner block mounting member 5438 is reinforced with ribs to withstand this rotational moment. Specifically, a pair of first ribs 5438c are provided at the corners formed by the side plate 5438a and the bottom plate 5438b at both ends of the runner block mounting member 5438 in the Y-axis direction. A second rib 5438d is provided.

Thus, the Z-axis runner block 5433 is fixed to the frame 5422 and is slidable with respect to the Z-axis rails 5437 . Therefore, the movable frame 5432 is slidable in the vertical direction, and movement of the movable frame 5432 in directions other than the vertical direction is restricted. In this way, since the moving direction of the movable frame 5432 is restricted only to the vertical direction, when the servo motor unit 150Z is driven to rotate the ball screw 5418, the movable frame 5432 and this movable frame 5432 are engaged. The table 5100 advances and retreats in the vertical direction.

Further, the third actuator 5400 is also provided with position detection means (not shown) similar to the position detection means 5250 (FIGS. 34 and 35) of the first actuator 5200 . The control unit C5 of the vibration test apparatus 5000 can control the height of the movable frame 5432 to be within a predetermined range based on the detection result of this position detection means (FIG. 38).

As described above, in this embodiment, two pairs of rails and an intermediate stage configured to be slidable with respect to the rails are provided between the actuators whose drive shafts are perpendicular to each other and the table 5100. there is As a result, the table 5100 can slide in any direction on a plane perpendicular to the driving direction of each actuator. Therefore, even if the table 5100 is displaced by a certain actuator, the load and moment caused by this displacement are not applied to the other actuators, and the other actuators and the table 5100 are engaged via the intermediate stage. is maintained. That is, even if the table is displaced to an arbitrary position, each actuator maintains a state in which the table can be displaced. Therefore, in this embodiment, the three actuators 5200, 5300, and 5400 can be simultaneously driven to vibrate the table 5100 and the work fixed thereon in three axial directions.

In this embodiment, as described above, between the actuators 5200, 5300, 5400 and the table 5100, there is provided a connecting portion having a guide mechanism combining rails and runner blocks. A similar guide mechanism is also provided on actuators 5200, 5300, 5400 and is used to guide the nut of the ball screw mechanism of each actuator.

Further, in each of the above-described embodiments, an ultra-low inertia servomotor is used as the torque generator, but the configuration of the present invention is not limited to this. The present invention also includes a configuration using another type of electric motor (for example, an inverter motor) that has a small moment of inertia of the rotor and can be driven at high acceleration or high jerk. In this case, as in the above-described embodiments, a configuration in which an encoder is provided in the electric motor and feedback control is performed based on the rotation state (for example, the number of rotations and the angular position) of the output shaft of the electric motor detected by the encoder can be adopted.

Further, the above-described embodiment is an example in which the present invention is applied mainly to an endurance test apparatus for a power transmission device for automobiles, but the present invention is not limited to this, and can be used for various purposes in general industries. can be done. For example, the present invention can be used to evaluate the mechanical properties and durability of motorcycles, agricultural machinery, construction machinery, railroad vehicles, ships, aircraft, power generation systems, water supply and drainage systems, or various parts that make up these. can.

Although the present embodiment has been described above, the present invention is not limited to the above configuration, and various modifications are possible within the scope of the technical idea of the present invention. For example, in each of the above embodiments, the servo motor unit 150 (or the torque applying servo motor unit 132 ) is used, it is also possible to use a servomotor unit in which one servomotor 150B and a plurality of two-axis output servomotors 150A are connected in three or more stages.

<Addendum>
In order to further expand the application range of servomotor type test equipment, there is a demand for higher output while maintaining the high acceleration characteristics of ultra-low inertia servomotors.

In addition, since the cost of the servomotor accounts for a large portion of the manufacturing cost of the servomotor type testing equipment, there is a need for a servomotor type testing equipment that can test multiple specimens at the same time using a single servomotor. there is

However, if the output of the servo motor is simply increased, it becomes necessary to increase the strength of each part of the servo motor. In addition, this increases the output ratio of the moment of inertia of the servomotor (the ratio of the moment of inertia to the output of the servomotor). There is a problem of lowering.

In addition, since conventional servo motors have only one output shaft, it is necessary to provide a gear mechanism or the like to distribute the power in order to enable testing of multiple specimens at the same time. There was a problem such as enlargement of the apparatus.

According to one embodiment of the present invention, a tubular body frame, a substantially flat plate-shaped first bracket attached to one axial end of the body frame, and a substantially flat bracket attached to the other axial end of the body frame a flat plate-shaped second bracket; and a drive shaft that passes through the hollow portion of the body frame, penetrates the first bracket and the second bracket, and is rotatably supported by bearings provided in the first bracket and the second bracket, respectively. , wherein one end of the drive shaft protrudes outside from the first bracket to serve as a first output shaft for outputting driving force to the outside, and the other end protrudes outside from the second bracket to serve as a second output shaft. There is provided a two-axis output servomotor characterized in that it is configured as

The first bracket and the second bracket may have a first mounting surface provided with a tapped hole for mounting the two-axis output servomotor on the opposite side of the surfaces facing each other.

The first bracket and the second bracket may have a second mounting surface perpendicular to the first mounting surface and provided with tapped holes for mounting the two-axis output servomotor.

At least one of the first bracket and the second bracket may be provided with a rotary encoder for detecting the rotational position of the drive shaft.

According to one embodiment of the present invention, a tubular body frame, a load-side bracket attached to one axial end of the body frame, and a non-load-side bracket attached to the other axial end of the body frame. a drive shaft that passes through the hollow portion of the body frame, penetrates the first bracket and the second bracket, and is rotatably supported by bearings provided in the load side bracket and the anti-load side bracket, respectively; A second servomotor that constitutes an output shaft that outputs a driving force to the outside with only one end protruding from the load side bracket, the above two-axis output servomotor, the load side bracket and the second bracket A coupling member that connects the output shaft of the second servomotor and the second output shaft of the two-axis output servomotor together, the second servomotor and the two-axis output servomotor. and a drive control section for driving in the same phase.

The above servo motor unit includes the above two-axis output servo motor, and a rotary encoder for detecting the rotational position of the drive shaft is attached to either one of the load-side bracket and the non-load-side bracket. may be configured to control the driving of the second servomotor and the two-axis output servomotor based on the signal output by the rotary encoder.

The servo motor unit includes the two-axis output servo motor, and the drive control unit is configured to control driving of the second servo motor and the two-axis output servo motor based on a signal output from one of the rotary encoders. may have been

According to one embodiment of the present invention, a first drive shaft to which one end of a work is attached and which rotates around a predetermined rotation axis, and a first drive shaft to which the other end of the work is attached and which rotates around the rotation axis are provided. 2 drive shafts, a load applying section that supports the first drive shaft and rotationally drives the first drive shaft to apply a torsional load to the workpiece, and at least one that supports the load applying section so as to be rotatable about the rotation axis. A first bearing, a rotary drive unit that rotationally drives the first drive shaft and the load applying unit in the same phase, and a torque sensor that detects a torsional load, wherein the rotary drive unit rotates the first drive shaft and the second drive shaft. The work is rotated via the shaft, and a load is applied to the work by giving a phase difference to the rotation of the first drive shaft and the second drive shaft by the load applying section. a frame having a cylindrical shaft portion into which the first drive shaft is inserted; the frame is supported by a first bearing at the shaft portion and supports the first drive shaft; There is provided a rotary torsion testing device that is attached to the portion inserted into the shaft portion and that is configured to detect the torsional load of the portion, wherein the load application portion includes the above servomotor unit.

The rotational torsion testing device includes a drive power supply unit that supplies drive power to the servo motor unit, and a drive power transmission line that transmits the drive power from the drive power supply unit to the servo motor unit, which are arranged outside the load application unit. a torque signal processing unit arranged outside the load applying unit for processing a torque signal output from the torque sensor; and a torque signal transmission line for transmitting the torque signal from the torque sensor to the torque signal processing unit. The power transmission line includes an externally driven power transmission line disposed outside the load applying section, an internally driven power transmission line disposed inside the load applying section and rotating together with the load applying section, the externally driven power transmission line and the internal a first slip ring portion for connecting the drive power transmission line, the torque signal transmission line being wired inside the load applying portion and the external torque signal transmission line arranged outside the load applying portion; An internal torque signal transmission line that rotates together with the applying section, and a second slip ring section that connects the external torque signal transmission line and the internal torque signal transmission line, wherein the second slip ring section is separated from the first slip ring section. It is good also as a structure arranged by doing.

The rotation driving section includes a second motor and a driving force transmission section that transmits the driving force of the second motor to the load applying section and the second drive shaft to rotate them in the same phase, and the driving force transmission section is the second motor. to the second drive shaft, and a second driving force transmission portion for transmitting the driving force of the second motor to the load applying portion.

A third driving shaft driven by a second motor, wherein the first driving force transmission unit and the second driving force transmission unit each include an endless belt mechanism, and the first driving force transmission unit is arranged in parallel with the rotation shaft a first drive pulley coaxially fixed to the third drive shaft; a first driven pulley coaxially fixed to the load applying portion; an endless belt, wherein the second driving force transmission part is connected to a fourth drive shaft coaxially connected to the third drive shaft, a second drive pulley fixed to the fourth drive shaft, and the first drive shaft; A configuration may include a fixed second driven pulley and a second endless belt that is stretched over the second drive pulley and the second driven pulley.

According to one embodiment of the present invention, there is provided a torsion testing device that applies torque to an input/output shaft of a test piece that is a power transmission device, and includes a first drive unit that is connected to the input shaft of the test piece; A second drive unit connected to the output shaft is provided, and the first drive unit and the second drive unit include the above-described servo motor unit, a speed reducer that reduces the rotation of the drive shaft of the servo motor unit, and a test object. A chuck to which an input shaft or an output shaft is attached and which transmits the output of the speed reducer to the input shaft or the output shaft of the test piece, and a torque sensor which transmits the output of the speed reducer to the chuck and detects the torque output by the speed reducer. and a tachometer for detecting the number of rotations of the chuck.

Equipped with a spindle that connects a torque sensor and a chuck, and a bearing that rotatably supports the spindle, the speed reducer includes a gear case, a bearing, and a gear mechanism supported by the gear case via the bearing. The load of the power transmission shaft including the gear mechanism of the speed reducer that transmits the driving force of the servomotor to the test piece, the torque sensor, and the spindle may be supported by the spindle and the gear mechanism of the speed reducer.

According to one embodiment of the present invention, there is provided a torsion testing apparatus for simultaneously testing a first specimen and a second specimen, wherein the two-axis output servomotor and the rotation of the first output shaft are rotated by the first specimen. A first drive transmission part that transmits to one end of the test piece, a first reaction force part that fixes the other end of the first test piece, and a second transmission that transmits the rotation of the second output shaft to one end of the second test piece. and a second reaction force portion that fixes the other end of the second test piece, and the first drive transmission portion and the second drive transmission portion A chuck device for attaching one end is provided, the first reaction force part and the second reaction force part are provided with a chuck device for attaching the other end of the first test piece or the second test piece, the first test piece or the second test piece A configuration including a torque sensor that detects the torque applied to the specimen may be employed.

The first drive transmission section and the second drive transmission section each include a reduction gear that reduces the rotation of the first output shaft or the second output shaft, and a rotary encoder that detects the rotation of the output shaft of the reduction gear. good too.

According to one embodiment of the present invention, a frame; A coupling that connects to the drive shaft, a first gripper that is fixed to the output shaft of the reduction mechanism and grips one end of the test piece, and a second grip that is fixed to the frame and grips the other end of the test piece A torsion testing device is provided comprising:

According to one embodiment of the present invention, the servomotor unit, the feed screw, the coupling connecting the feed screw and the drive shaft of the servomotor unit, the nut engaged with the feed screw, and the movement of the nut A linear actuator is provided that includes a linear guide that limits its direction to the axial direction of the feed screw, and a support plate to which the servomotor and linear guide are fixed.

According to one embodiment of the present invention, a table for attaching a workpiece and a first actuator capable of vibrating the table in a first direction are provided, and the first actuator includes the above-described servo motor unit and a servo and a ball screw mechanism for converting rotational motion of the motor unit into translational motion in a first direction or a second direction.

According to one embodiment of the present invention, a table for attaching a workpiece, a first actuator capable of vibrating the table in a first direction, and a table that vibrates in a second direction orthogonal to the first direction are provided. a swingable second actuator; first connecting means for slidably connecting the table to the first actuator in the second direction; and slidably connecting the table to the second actuator in the first direction. and a second coupling means, wherein the first actuator and the second actuator are the above-described servo motor unit and a ball screw mechanism for converting rotational motion of the servo motor unit into translational motion in a first direction or a second direction. and a vibrating device respectively provided.

According to one embodiment of the present invention, a table for attaching a workpiece, a first actuator capable of vibrating the table in a first direction, and a table that vibrates in a second direction orthogonal to the first direction are provided. a second actuator capable of vibrating; a third actuator capable of vibrating the table in a third direction perpendicular to both the first direction and the second direction; a first connecting means for slidably connecting the table in the first direction and the third direction; a second connecting means for connecting the table to the second actuator so as to be slidable in the first direction and the third direction; and a third connecting means for slidably connecting the three actuators in the first direction and the second direction, wherein the first actuator, the second actuator and the third actuator are connected to the above servo motor unit and the servo motor unit. and a ball screw mechanism for converting rotational motion of the motor unit into translational motion in a first direction, a second direction, or a third direction.

According to one embodiment of the present invention, a first servomotor, a tubular casing, a second servomotor fixed in the casing, and a frame fixed in the casing and the output shaft of the servomotor are connected. A torque applying unit having a speed reducer having an input shaft and an output shaft that decelerates and outputs rotation of the input shaft and protrudes from a casing, and a test object is attached and one end is connected to the output shaft of the speed reducer A first shaft, a second shaft one end of which is connected to the output shaft of the motor, and a connection portion to which the output shaft of the speed reducer and the casing of the torque applying unit are connected, and have a gear that rotates the output shaft and the casing. and a connection portion where the other end of the first shaft and the other end of the second shaft are connected, and the rotational motion of the first shaft and the second shaft is transmitted by gears A torsion test apparatus is provided comprising: a second gearbox that performs

According to the present invention, since the power is circulated through the first gear box and the second gear box, compared with the conventional configuration in which the power is circulated by the belt mechanism, the power loss is reduced and the running speed is reduced. A lower cost torsion tester is achieved.

According to one embodiment of the present invention, an output shaft, a control section for controlling rotation of the output shaft so as to generate a simulated power simulating a predetermined power, and a torque instructed by the control section is applied to the output shaft. , a weight applying unit rotatably supported, and a rotation driving unit that rotates the load applying unit at a rotational speed instructed by the control unit. A power simulator is provided with a servomotor.

According to the configuration of the embodiment of the present invention, there is provided an electric power simulator capable of accurately simulating torque fluctuations of high frequency components even at high rotational speeds.

By using both ends of the drive shaft as the first output shaft and the second output shaft, respectively, it is possible to distribute the output without adding a power distribution means such as a gear mechanism, and the friction accompanying the addition of the power distribution means becomes possible. An increase in resistance and an increase in the size of the test equipment are prevented. In addition, with this configuration, it is possible to connect one of the first output shaft and the second output shaft to the output shaft of another servomotor to synthesize the output. It is possible to achieve high output while suppressing deterioration in acceleration characteristics due to an increase in .

Claims (22)

A mechanism that rotatably supports a wheel on which a tire as a specimen is mounted and presses the tread portion of the tire against a simulated road surface;
a torque applying unit for applying torque to the wheel;
a first electric motor that rotationally drives the torque applying unit;
with
The torque applying unit is
a casing rotationally driven by the first electric motor;
a second electric motor attached to the casing;
a connecting shaft that is rotationally driven by the second electric motor,
The second electric motor has a rated output of 10 kW or more and a moment of inertia of the rotating part of 10 ⁻² kg·m ² or less.
tire testing equipment. A mechanism that rotatably supports a wheel on which a tire as a specimen is mounted and presses the tread portion of the tire against a simulated road surface;
a torque applying unit for applying torque to the wheel;
a first electric motor that rotationally drives the torque applying unit;
with
The torque applying unit is
a casing rotationally driven by the first electric motor;
a second electric motor attached to the casing;
wherein the shaft of the second electric motor is arranged concentrically with the rotation axis of the casing;
tire testing equipment. wherein the torque applying unit comprises a connecting shaft that is rotationally driven by the second electric motor;
A tire testing device according to claim 2. the torque applying unit comprises a bearing that rotatably supports the casing;
The casing has a cylindrical shaft portion rotatably supported by the bearing portion,
A bearing that rotatably supports the connecting shaft passed through the hollow portion of the shaft is provided on the inner circumference of the shaft,
The tire testing device according to claim 1 or 3. A mechanism that rotatably supports a wheel on which a tire as a specimen is mounted and presses the tread portion of the tire against a simulated road surface;
a torque applying unit for applying torque to the wheel;
a first electric motor that rotationally drives the torque applying unit;
with
The torque applying unit is
a casing rotationally driven by the first electric motor;
a bearing that rotatably supports the casing;
a second electric motor attached to the casing;
a connecting shaft that is rotationally driven by the second electric motor,
The connecting shaft is arranged concentrically with the rotation axis of the casing,
The casing is
having a cylindrical shaft,
rotatably supported by the bearing on the shaft;
A bearing that rotatably supports the connecting shaft passed through the hollow portion of the shaft is provided on the inner circumference of the shaft,
tire testing equipment. A torque sensor that detects the torque of the connecting shaft,
wherein the torque sensor comprises a strain gauge attached to a portion of the connecting shaft accommodated within the shaft portion,
The tire testing device according to claim 4 or 5. A mechanism that rotatably supports a wheel on which a tire as a specimen is mounted and presses the tread portion of the tire against a simulated road surface;
a torque applying unit for applying torque to the wheel;
a first electric motor that rotationally drives the torque applying unit;
with
The torque applying unit is
a casing rotationally driven by the first electric motor;
a second electric motor attached to the casing;
a connecting shaft rotationally driven by the second electric motor;
a bearing that rotatably supports the casing;
and a torque sensor that detects the torque of the connecting shaft,
The casing has a cylindrical shaft portion rotatably supported by the bearing portion,
A bearing is provided on the inner periphery of the shaft portion to rotatably support the connecting shaft passed through the hollow portion of the shaft portion,
wherein the torque sensor comprises a strain gauge attached to a portion of the connecting shaft accommodated within the shaft portion,
tire testing equipment. A constricted portion is formed in a portion of the connecting shaft accommodated in the shaft portion, and the strain gauge is attached to the constricted portion.
The tire testing device according to claim 6 or 7. a control unit that controls the first electric motor and the second electric motor;
a rotation speed measuring unit that measures the rotation speed of the torque applying unit;
with
The control unit
controlling the driving of the first electric motor based on the measurement result of the rotation speed measuring unit;
controlling the driving of the second electric motor based on the detection result of the torque sensor;
A tire testing device according to any one of claims 6 to 8. The casing is cylindrical,
wherein the second electric motor is disposed within the hollow portion of the casing;
A tire testing device according to any one of claims 1 to 9. wherein the shaft of the second electric motor is arranged concentrically with the rotation axis of the casing;
11. The tire testing device of claim 10. the second electric motor comprises a motor case,
wherein the motor case is fixed to the casing via a plurality of fixing rods;
A tire testing device according to any one of claims 1 to 11. The motor case comprises a bracket provided with a second bearing that rotatably supports the shaft of the second electric motor,
one end of the fixed rod is fixed to the bracket;
13. The tire testing device of claim 12. the casing comprises a cylindrical body that houses the second electric motor,
The other end of the fixed rod is fixed to the trunk,
14. The tire testing device of claim 13. wherein the torque applying unit comprises a speed reducer that reduces rotation of the second electric motor;
The speed reducer is
Equipped with a mounting flange,
fixed to the casing by sandwiching and tightening the mounting flange between the body and the shaft;
15. A tire testing apparatus as claimed in claim 14 indirectly citing any of claims 4-7. a belt mechanism for transmitting the power of the first electric motor to the torque applying unit;
The casing has a pulley portion around the outer circumference of which the belt of the belt mechanism is wound,
A tire testing device according to any one of claims 1 to 15. a power supply unit disposed outside the casing for supplying power to the second electric motor;
a power transmission line that transmits power from the power supply unit to the second electric motor;
with
The power transmission line is
an external power transmission line arranged outside the casing;
an internal power transmission line disposed inside the casing and rotatable with the casing;
a slip ring unit that connects the external power transmission line and the internal power transmission line,
A tire testing device according to any one of claims 1 to 16. Equipped with an alignment control mechanism capable of adjusting the alignment of the wheel,
A tire testing device according to any one of claims 1 to 17. The alignment control mechanism is
A tire load adjustment unit that adjusts the tire load by moving the position of the rotation axis of the wheel in a direction perpendicular to the simulated road surface,
19. The tire testing device of claim 18. The alignment control mechanism is
A slip angle adjustment unit that can adjust the slip angle of the tire with respect to the simulated road surface by tilting the rotation axis of the wheel around the perpendicular to the simulated road surface,
A tire testing device according to claim 18 or claim 19. The alignment control mechanism is
A camber angle adjustment unit that can adjust the camber angle by tilting the rotation axis of the wheel with respect to the simulated road surface,
21. A tire testing device according to any one of claims 18-20. Equipped with a traverse device that moves the wheel in the direction of its rotation axis,
22. A tire testing device according to any one of claims 18-21.

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