Load application section and mechanical testing device

Abstract

To control a torque separately from the number of rotations.SOLUTION: The load provision unit according to an embodiment of the present invention includes: a casing rotatably supported; and an electric motor mounted to the casing. The drive amount of the electric motor is controllable and the casing is connectable to driving means in the outside. The electric motor can output rotations generated by the electric motor added to rotations provided to the casing by the external driving means.SELECTED DRAWING: Figure 15

Description

Technical Field

[0001] The present invention relates to a tire test apparatus.

Background Art

[0002] The inventors of the present invention have adopted an ultra-low inertia servo motor with significantly reduced inertia compared to conventional servo motors, thereby enabling various fatigue test apparatuses and vibration test apparatuses of the servo motor type that can apply high-frequency repetitive loads of several tens to several hundreds of Hz to be put into practical use (for example, Patent Document 1).

[0003] The above servo motor type test apparatus has rapidly expanded its scope of application because it solves many serious problems that conventional hydraulic test apparatuses have (for example, the installation of large-scale hydraulic supply facilities such as oil tanks and hydraulic piping is required, regular replacement of a large amount of hydraulic oil is required, and the working environment and soil are polluted due to leakage of hydraulic oil).

Prior Art Documents

Patent Documents

[0004]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0005] An object of the present invention is to provide a tire test apparatus capable of testing a tire that simulates an actual driving state.

Means for Solving the Problems

[0006] According to one embodiment of the present invention, a tire testing apparatus is provided, comprising: a rotating drum having a simulated road surface formed on its outer surface; a mechanism that rotatably supports a tire, which is a test specimen, while mounted on a wheel, and presses the tread portion of the tire against the simulated road surface; a torque application unit that applies torque to the tire; and a rotational drive motor that rotationally drives the casings of the rotating drum and the torque application unit.

[0007] In the tire testing apparatus described above, the torque application unit may be configured to include a servo motor fixed to the casing, and the casing of the torque application unit may be rotatably supported concentrically with the output shaft of the servo motor.

[0008] The above-described tire testing apparatus may also be configured to include a power transmission unit that transmits the driving force of the motor to the rotating drum and the torque application unit, thereby rotating the rotating drum and the tire at the same peripheral speed.

[0009] In the tire testing apparatus described above, the power transmission section may be configured to include at least one of an endless belt mechanism and a gear mechanism.

[0010] In the tire testing apparatus described above, the mechanism that presses the tire tread against the simulated road surface may be configured as an alignment control mechanism capable of adjusting the tire's alignment with respect to the simulated road surface.

[0011] In the above-described tire testing apparatus, the alignment control mechanism may be configured to include a tire load adjustment unit that adjusts the tire load by moving the position of the tire's rotation axis in the radial direction of the rotating drum.

[0012] In the tire testing apparatus described above, the alignment control mechanism may be configured to include a slip angle adjustment unit that can adjust the slip angle of the tire relative to the simulated road surface by tilting the rotation axis of the tire around a perpendicular line to the simulated road surface.

[0013] In the above tire test device, the alignment control mechanism may be configured to include a camber angle adjustment unit capable of adjusting the camber angle by inclining the rotation axis of the tire with respect to the rotation axis of the rotating drum.

[0014] In the above tire test device, it may be configured to include a traversing device for moving the tire in the rotation axis direction.

[0015] In the above tire test device, the rotation drive motor may be an inverter motor.

Advantages of the Invention

[0016] According to the configuration of an embodiment of the present invention, it becomes possible to test a tire that simulates an actual driving state.

Brief Description of the Drawings

[0017] [Figure 1] It is a side view of a two-axis output servo motor according to an embodiment of the present invention. [Figure 2] It is a side view of a servo motor unit according to an embodiment of the present invention. [Figure 3] It is a longitudinal sectional view of a modified example of a servo motor unit according to an embodiment of the present invention. [Figure 4] It is a side view of a rotational torsion test device according to a first embodiment of the present invention. [Figure 5] It is a longitudinal sectional view near the load applying portion of a rotational torsion test device according to a first embodiment of the present invention. [Figure 6] It is a block diagram showing a schematic configuration of a control system of a rotational torsion test device according to a first embodiment of the present invention. [Figure 7] It is an external view of a power simulator according to a modified example of a first embodiment of the present invention. [Figure 8] It is an external view of a power simulator according to a modified example of a first embodiment of the present invention. [Figure 9] It is a side view of a test device provided with a power simulator according to a modified example of a first embodiment of the present invention. [Figure 10] It is a partially enlarged view of a test apparatus equipped with a power simulator according to a modified example of the first embodiment of the present invention. [Figure 11] It is a plan view of a rotational torsion test apparatus according to the second embodiment of the present invention. [Figure 12] It is a side view of a rotational torsion test apparatus according to the second embodiment of the present invention. [Figure 13] It is a longitudinal sectional view near the load applying portion of a rotational torsion test apparatus according to the second embodiment of the present invention. [Figure 14] It is a top view and a side view of a torsion test apparatus according to the third embodiment of the present invention. [Figure 15] It is a side sectional view of the torque applying portion of a torsion test apparatus according to the third embodiment of the present invention. [Figure 16] It is a top view of a torsion test apparatus according to the fourth embodiment of the present invention. [Figure 17] It is a top view of a torsion test apparatus according to the fifth embodiment of the present invention. [Figure 18] It is a top view of a torsion test apparatus according to the sixth embodiment of the present invention. [Figure 19] It is an external view of a rotational torsion test apparatus according to the seventh embodiment of the present invention. [Figure 20] It is an external view of a rotational torsion test apparatus according to the eighth embodiment of the present invention. [Figure 21] It is a top view of a tire wear test apparatus according to the ninth embodiment of the present invention. [Figure 22] It is an external view of a tire test apparatus according to the tenth embodiment of the present invention. [Figure 23] It is an external view of a tire test apparatus according to the tenth embodiment of the present invention. [Figure 24] It is an external view of a power absorption type durability test apparatus for an FR transmission according to the eleventh embodiment of the present invention. [Figure 25] It is an external view of a power absorption type durability test apparatus for an FF transmission according to the twelfth embodiment of the present invention. [ [Figure 26] It is a side view of a torsion test apparatus according to the thirteenth embodiment of the present invention. [Figure 27] This is a side view of the first drive unit of the 13th embodiment of the present invention. [Figure 28] This is a plan view of a torsion testing apparatus according to a first modified example of the 13th embodiment of the present invention. [Figure 29] This is a plan view of a torsion testing apparatus according to a second modified example of the thirteenth embodiment of the present invention. [Figure 30] This is a plan view of a torsion testing apparatus according to a third modified example of the thirteenth embodiment of the present invention. [Figure 31] This is a side view of a torsion testing apparatus according to the 14th embodiment of the present invention. [Figure 32] This is an enlarged view of the drive unit of the 14th embodiment of the present invention. [Figure 33] This is a top view of a vibration testing apparatus according to the 15th embodiment of the present invention. [Figure 34] This is a side view of the first actuator according to the 15th embodiment of the present invention, as seen from the Y-axis direction. [Figure 35] This is a top view of the first actuator according to the 15th embodiment of the present invention. [Figure 36] This is a side view of the table and third actuator of the 15th embodiment of the present invention, as seen from the X-axis direction. [Figure 37] This is a side view of the table and third actuator of the 15th embodiment of the present invention, as seen from the Y-axis direction. [Figure 38] This is a block diagram of the control system in a vibration testing apparatus according to the 15th embodiment of the present invention. [Modes for carrying out the invention]

[0018] Embodiments of the present invention will be described below with reference to the drawings.

[0019] (First Embodiment) First, a two-axis output servo motor 150A according to an embodiment of the present invention will be described. Figure 1 is a side view of the two-axis output servo motor 150A. The two-axis output servo motor 150A is a high-output (rated output 37kW) ultra-low inertia servo motor equipped with two output shafts 150A2a and 150A2b. The two-axis output servo motor 150A comprises a main frame 150A1, a drive shaft 150A2, a first bracket 150A3, and a second bracket 150A4.

[0020] The main frame 150A1 is a roughly cylindrical frame, and a stator (not shown) having a coil is provided on its inner circumference. A first bracket 150A3 and a second bracket 150A4 are attached to both axial ends of the main frame 150A1, respectively, so as to close the openings of the main frame 150A1. The main frame 150A1, the first bracket 150A3, and the second bracket 150A4 form the motor case. The first bracket 150A3 and the second bracket 150A4 are provided with bearings 150A3b and 150A4b, respectively, which rotatably support the drive shaft 150A2. A rotor (not shown) is provided on the outer circumference of the longitudinal center of the drive shaft 150A2, and rotational force is applied to the drive shaft 150A2 by the interaction between the rotating magnetic field generated by the stator and the rotor provided on the drive shaft 150A2.

[0021] One end 150A2a (the rightmost end in Figure 1) of the drive shaft 150A2 passes through the first bracket 150A3 and protrudes outward from the motor case, becoming the output shaft 150A2a. The other end 150A2b of the drive shaft 150A2 passes through the second bracket 150A4 and protrudes outward from the motor case, becoming the second output shaft 150A2b. The second bracket 150A4 incorporates a rotary encoder (not shown) that detects the rotation of the other end 150A2b of the drive shaft 150A2.

[0022] Furthermore, the lower surfaces of the first bracket 150A3 and the second bracket 150A4 are provided with a pair of tapped holes 150A3t and 150A4t, respectively, for fixing the two-axis output servo motor 150A. In conventional servo motors, fixing tapped holes extending parallel to the drive shaft were provided only on the mounting surface (right side in Figure 1) of the bracket on the load side (the side from which the output shaft protrudes). For applications other than precision mechanical testing, fixing by tapped holes on the mounting surface of the load-side bracket is sufficient. However, in precision mechanical testing equipment (e.g., fatigue testing equipment and vibration testing equipment) that applies dynamic loads of several tens of Hz (e.g., 20 Hz) or higher, when using a high-output servo motor with a rated output of about 10 kW or more, fixing by the mounting surface of the bracket alone is insufficient to completely fix the servo motor perpendicular to the drive shaft. This results in vibrations with minute amplitudes of several μm to several tens of μm, for example, causing non-negligible errors in the test results.

[0023] The inventors, through numerous vibration analyses and experiments, have found that adding two tapped holes for fixing, extending perpendicular to the drive shaft, to the underside of each bracket significantly improves vibration noise (for example, by an order of magnitude). By providing tapped holes on the underside of each bracket, in addition to the mounting surface of the load-side bracket, and using these tapped holes to fix the servo motor with bolts, vibration noise is reduced, enabling more precise mechanical testing.

[0024] Furthermore, the servo motor 150A has a high rated output of 37kW and generates a large amount of heat during operation, so it is configured to dissipate the heat generated internally to the outside by water cooling. Two tube fittings 150A6 are provided on the upper part of the main frame 150A1 to which external piping for supplying and discharging cooling water is connected.

[0025] In this embodiment, a servo motor unit 150 is used in which the two-axis output servo motor 150A described above and a servo motor 150B having one output shaft 150B2a are connected in series. Figure 2 is a side view of the servo motor unit 150 according to an embodiment of the present invention. The servo motor unit 150 has one drive shaft 152.

[0026] In the following description of the servo motor unit 150, the side on which the drive shaft 152 protrudes (the right side in Figure 2) is referred to as the load side, and the opposite side as the non-load side. The two-axis output servo motor 150A and servo motor 150B each generate a torque of up to 350 N·m, and the moment of inertia of the rotating part is 10 -2 (kg·m 2 This is a high-power, ultra-low inertia servo motor with a rated output of 37kW, with the following characteristics:

[0027] The servo motor 150B comprises a main frame 150B1, a drive shaft 150B2, a load-side bracket 150B3, a non-load-side bracket 150B4, and a rotary encoder 150B5. The main frame 150B1 and the load-side bracket 150B3 are identical to the main frame 150A1 and the first bracket 150A3 of the two-axis output servo motor 150A. The upper part of the main frame 150B1 is provided with two tube fittings 150B6 to which external piping for supplying and discharging cooling water is connected. The non-load-side bracket 150B4 has a configuration that is almost identical to the second bracket 150A4 of the two-axis output servo motor 150A, but it does not have a built-in rotary encoder. As described later, the rotary encoder 150B5 is externally attached to the non-load-side bracket 150B4. In addition, a pair of tapped holes 150B3t and 150B4t are provided on the lower surfaces of the load-side bracket 150B3 and the non-load-side bracket 150B4, respectively.

[0028] One end 150B2a of the drive shaft 150B2 on the load side passes through the load-side bracket 150B3 and protrudes outward from the motor case, becoming the output shaft 150B2a. On the other hand, a rotary encoder 150B5 for detecting the angular position of the drive shaft 150B2 is mounted on the mounting surface (left side in Figure 2) of the non-load-side bracket 150B4, and the other end 150B2b of the drive shaft 150B2 passes through the non-load-side bracket 150B4 and is housed inside the rotary encoder.

[0029] As shown in Figure 2, the output shaft 152B2a of the servo motor 150B and the second output shaft 150A2b of the two-axis output servo motor 150A are connected by a coupling 150C. In addition, the load-side bracket 150B3 of the servo motor 150B and the second bracket 150A4 of the two-axis output servo motor 150A are connected by a connecting flange 150D at a predetermined distance apart.

[0030] The connecting flange 150D has a cylindrical body portion 150D1 and two flange portions 150D2 that extend radially outward from both axial ends of the body portion 150D1. Each flange portion 150D2 is provided with through holes for bolt fixing at positions corresponding to tapped holes provided on the mounting surfaces of the load-side bracket 150B3 and the second bracket 150A4, and is fixed to the load-side bracket 150B3 and the second bracket 150A4 with bolts.

[0031] The servo motor unit 150 is equipped with two rotary encoders for detecting the angular position of the drive shaft 150B2 (one built into the second bracket 150A4 of the two-axis output servo motor 150A, and the other rotary encoder 150B5 attached to the non-load side bracket 150B4 of the servo motor 150B). However, normally only one rotary encoder is used for drive control of the servo motor unit 150, while the other is used for maintenance and monitoring the drive status.

[0032] For example, vibration tests and durability tests (rotational torsion tests) of power transmission devices require large shaft torques that fluctuate at high speeds (high frequencies). To generate such large torques that fluctuate at high frequencies, a motor with a small rotor moment of inertia (inertia) and high capacity (high output) is required. To realize such a servo motor, the rotor needs to be elongated. However, if the rotor is made elongated beyond a certain point, the rigidity of the rotor (rotating shaft) decreases, causing significant vibrations of the rotor that cause it to bend in an arc shape, preventing the motor from operating normally. Therefore, in the conventional configuration where the rotating shaft is supported only at both ends by a pair of bearings, there were limitations to increasing capacity while maintaining a low moment of inertia.

[0033] In this embodiment, the servo motor unit 150 has a long rotor connected by a coupling 150C, which is supported by bearings at a total of four points: both ends in the longitudinal direction and two points near the connection point. As a result, even if the rotor is lengthened, it is held with high rigidity and can operate stably, making it possible to generate large torques that fluctuate at high frequencies, which was not possible with conventional servo motors. For example, the servo motor unit 150 alone (no load) can generate 30,000 rad / s 2 The above angular accelerations are achievable.

[0034] In this embodiment, the servo motor unit 150 is configured to connect two servo motors (two motor cases and two rotating shafts). However, as shown in Figure 3, one or more bearings may be provided in the middle of the longitudinal direction of a pair of long motors, and the drive shaft may be supported at both ends and at one or more points in the middle.

[0035] Next, the configuration of the rotary torsion testing apparatus 1 according to the first embodiment of the present invention will be described. Figure 4 is a side view of the rotary torsion testing apparatus 1 according to the first embodiment of the present invention. The rotary torsion testing apparatus 1 is a device that performs a rotary torsion test using an automobile clutch as the test specimen T1, and can apply a fixed or variable torque set between the input shaft and output shaft (for example, the clutch cover and the clutch disc) of the test specimen T1 while rotating the test specimen T1. The rotary torsion testing apparatus 1 includes a frame 10 that supports each part of the rotary torsion testing apparatus 1, a load application unit 100 that applies a predetermined torque to the test specimen T1 while rotating together with the test specimen T1, bearing units 20, 30 and 40 that rotatably 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 rotational speed of the load application unit 100, and an inverter motor 80, a drive pulley 91 and a drive belt (timing belt) 92 that rotate the load application unit 100 in a set rotational direction and rotational speed.

[0036] The frame 10 has a lower base plate 11 and an upper base plate 12 arranged horizontally in a vertical configuration, and a plurality of vertical support walls 13 connecting the lower base plate 11 and the upper base plate 12. A plurality of vibration-damping mounts 15 are attached to the lower surface of the lower base plate 11, and the frame 10 is placed on a flat floor F via the vibration-damping mounts 15. An inverter motor 80 is fixed to the upper surface of the lower base plate 11. In addition, bearings 20, 30, 40 and a rotary encoder 70 are attached to the upper surface of the upper base plate 12.

[0037] Figure 5 is a longitudinal cross-sectional view of the load application section 100 of the rotary torsion testing apparatus 1. The load application section 100 comprises a stepped cylindrical casing 100a, a servo motor unit 150, a reduction gear 160, and a connecting shaft 170 mounted inside the casing 100a, and a torque sensor 172. The casing 100a comprises a motor housing section (body section) 110 that houses the servo motor unit 150, a shaft section 120 rotatably supported by a bearing section 20, a shaft section 130 rotatably supported by a bearing section 30, and a shaft section 140 to which the slip ring 51 of the slip ring section 50 (Figure 4) is attached. The motor housing section 110 and the shaft sections 120, 130, and 140 are each substantially cylindrical (or stepped cylindrical) members with hollow sections (or whose diameter changes in a stepped manner in the axial direction). The motor housing 110 is the largest outer diameter component, housing the servo motor unit 150 in its hollow section. A shaft 120 is connected to one end of the motor housing 110 on the test specimen T1 side (the right end in Figure 5), and a shaft 130 is connected to the other end. A shaft 140 is connected to the end of the shaft 130 opposite to the motor housing 110. The shaft 140 is rotatably supported at its tip (the left end in Figure 4) by a bearing 40.

[0038] As shown in Figure 5, the servo motor unit 150 is fixed to the motor housing 110 by a plurality of fixing rods 111. Each fixing rod 111 is screwed into the tapped hole 150B3t provided in the load-side bracket 150B3 of the servo motor 150B, the tapped hole 150B4t provided in the non-load-side bracket 150B4, the tapped hole 150A3t provided in the first bracket 150A3 of the two-axis output servo motor 150A, and the tapped hole 150A4t provided in the second bracket 150A4, respectively, as shown in Figure 2.

[0039] The drive shaft 152 of the servo motor unit 150 is connected to the input shaft of the reduction gear 160 via a coupling 154. A connecting shaft 170 is connected to the output shaft of the reduction gear 160. The reduction gear 160 is equipped with a mounting flange 162, and the reduction gear 160 is fixed to the casing 100a by sandwiching the mounting flange 162 between the motor housing 110 and the shaft 120, and then tightening the motor housing 110 and the shaft 120 with bolts (not shown).

[0040] The shaft portion 120 is a roughly stepped cylindrical member, having a pulley portion 121 with a large outer diameter on the motor housing portion 110 side, and a main shaft portion 122 that is rotatably supported by a bearing portion 20 on the test specimen T1 side. As shown in Figure 4, a drive belt 92 is wrapped around the outer circumferential surface of the pulley portion 121 and the drive pulley 91 attached to the drive shaft 81 of the inverter motor 80, and the driving force of the inverter motor 80 is transmitted to the pulley portion 121 by the drive belt 92, causing the load application portion 100 to rotate. In addition, the pulley portion 121 houses the connection portion between the reduction gear 160 and the connecting shaft 170. By utilizing the portion that needs to have a larger outer diameter to accommodate this connection portion as the pulley, a compact device structure is realized without increasing the number of parts.

[0041] A torque sensor 172 is attached to the tip of the main shaft portion 122 of the shaft portion 120 (the rightmost end in Figure 5). One side of the torque sensor 172 (the right side in Figure 5) serves as a seating surface for attaching the input shaft (clutch cover) of the test specimen T1, and the torque applied to the test specimen T1 is detected by the torque sensor 172.

[0042] Bearings 123 and 124 are provided near both axial ends on the inner circumferential 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 the bearings 123 and 124. The torque sensor 172 is formed in a substantially cylindrical shape with a hollow portion, and the tip of the connecting shaft 170 (right end in Figure 5) 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 in the shaft hole of the clutch disc (clutch hub), which is the output shaft of the test specimen T1. That is, by rotating the connecting shaft 170 relative to the casing 100a of the load application portion 100 using the servo motor unit 150, a set dynamic or static torque can be applied between the input shaft (clutch cover) of the test specimen T1 fixed to the casing 100a and the output shaft (clutch disc) of the test specimen T1 fixed to the connecting shaft 170.

[0043] Furthermore, as shown in Figure 4, a rotary encoder 70 for detecting the rotational speed of the load application unit 100 is located near the end of the shaft portion 130 (the left end in Figure 4).

[0044] A slip ring 51 of the slip ring section 50 is attached to the axial center of the shaft section 140. A power line 150W (Figure 5) that supplies drive current to the servo motor unit 150 is connected to the slip ring 51. The power line 150W extending from the servo motor unit 150 is connected to the slip ring 51 through the hollow sections formed in the shaft sections 130 and 140.

[0045] The slip ring section 50 comprises a slip ring 51, a brush holder 52, and four brushes 53. As described above, the slip ring 51 is attached to the shaft 140 of the load-applying section 100. The brushes 53 are fixed to the bearing section 40 by the brush holder 52. The slip ring 51 has four electrode rings 51r arranged at equal intervals in the axial direction, and each brush 53 is positioned opposite each electrode ring 51r. Each electrode ring 51r is connected to each power line 150W of the servo motor unit 150, and each brush 53 is connected to the servo motor drive unit 330 (described later). That is, each power line 150W of the servo motor unit 150 is connected to the servo motor drive unit 330 via the slip ring section 50. The slip ring section 50 introduces the drive current of the servo motor unit 150 supplied by the servo motor drive unit 330 into the interior of the rotating load-applying section 100.

[0046] Furthermore, a slip ring (not shown) of the slip ring section 60 is attached to the tip of the shaft section 140 (the left end in Figure 4). A communication line 150W' (Figure 5) extending from the servo motor unit 150 is connected to the slip ring of the slip ring section 60, and signals from, for example, the torque sensor 172 or the rotary encoder 150B5 (Figure 2) built into the servo motor unit 150 are output to the outside via the slip ring section 60. If a large current, such as the drive current of a large-capacity motor, flows through the slip ring, a large amount of electromagnetic noise is likely to be generated due to discharge. Also, since the slip ring is not sufficiently shielded, it is susceptible to interference from electromagnetic noise. As described above, by connecting the communication line 150W', which carries a weak current, and the power line 150W, which carries a large current, to the external wiring using separate slip rings placed at a certain distance apart, the intrusion of noise into the communication signal is effectively prevented. Furthermore, in this embodiment, the slip ring portion 60 is provided on the side of the bearing portion 40 opposite to the slip ring portion 50 side. This configuration also provides the effect of shielding the slip ring portion 60 from electromagnetic noise generated in the slip ring portion 50 by the bearing portion 40.

[0047] Next, the control system of the rotary torsion testing apparatus 1 will be described. Figure 6 is a block diagram showing the schematic configuration of the control system of the rotary torsion testing apparatus 1. The rotary torsion testing apparatus 1 includes a control unit C1 that controls the entire rotary torsion testing apparatus 1, a setting unit 370 for setting test conditions, a waveform generation unit 320 that calculates the waveform of the drive amount of the servo motor unit 150 based on the set test conditions (such as the torque applied to the test specimen and the waveform of the twist angle) and outputs it to the control unit C1, a servo motor drive unit 330 that generates the drive current of the servo motor unit 150 based on the control of the control unit C1, an inverter motor drive unit 340 that generates the drive current of the inverter motor 80 based on the control of the control unit C1, a torque measurement unit 350 that calculates the torque applied to the test specimen based on the signal of the torque sensor 172, and a rotation speed measurement unit 360 that calculates the rotation speed of the load application unit 100 based on the signal of the rotary encoder 70.

[0048] The configuration 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, and GPIB (General Purpose Interface Bus) and USB (Universal The device is equipped with an external input interface such as a Serial Bus and a network interface. The setting unit 370 sets the test conditions based on user input received via the user input interface, data read from a replaceable recording medium, data input from an external device (e.g., a function generator) via the external input interface, and / or data acquired from a server via the network interface. The rotary torsion test apparatus 1 of this embodiment supports two control methods: displacement control, which controls the torsion applied to the test specimen T1 based on the torsion angle applied to the test specimen T1 (i.e., the amount of drive of the servo motor unit 150 detected by the rotary encoder 150B5 built into the servo motor unit 150), and torque control, which controls the torsion applied to the test specimen T1 (i.e., detected by the torque sensor 172). The setting unit 370 can set which control method to use.

[0049] The control unit C1 commands the inverter motor drive unit 340 to rotate the inverter motor 80 based on the set value of the rotational speed of the test specimen T1 obtained from the setting unit 370. 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 obtained from the waveform generation unit 320.

[0050] As shown in Figure 6, the torque measurement unit 350 calculates the torque value based on the signal from the torque sensor 172 and sends it to the control unit C1 and the waveform generation unit 320. The signal from the built-in rotary encoder in the servo motor unit 150 is also sent to the control unit C1, the waveform generation unit 320, and the servo motor drive unit 330. The waveform generation unit 320 calculates the rotational speed of the servo motor unit 150 from the signal from the built-in rotary encoder, which detects the rotation angle of the drive shaft 152 of the servo motor unit 150. In the case of torque control, the waveform generation unit 320 compares the set value of torque (or the drive amount of the servo motor unit 150 in the case of displacement control) with the measured value and corrects the set value of the drive amount of the servo motor unit 150 that is sent to the control unit C1 so that the two values ​​match.

[0051] Furthermore, the rotational speed measurement unit 360 calculates the rotational speed of the load application unit 100 based on the signal from the rotary encoder 70, and sends this measured value to the control unit C1. The control unit C1 compares the set value and the measured value of the rotational speed of the load application unit 100, and uses feedback control to adjust the frequency of the drive current sent to the inverter motor 80 so that the two values ​​match.

[0052] Furthermore, 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 provides feedback control to the drive current sent to the servo motor unit 150 so that the drive amount approaches the target value.

[0053] Furthermore, the control unit C1 is equipped with a hard disk drive (not shown) for storing test data, and records the rotational speed of the test specimen T1, the twist angle applied to the test specimen T1 (the rotation angle of the servo motor unit 150), and the torsional load data on the hard disk drive. The time variation of each measurement 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 automotive clutch as the test specimen T1.

[0054] In the rotary torsion testing apparatus 1 described above, the output of the inverter motor 80 for rotational speed control and the output of the servo motor unit 150 for torque control are coupled, enabling independent and highly accurate control of both rotational speed and torque. In particular, by newly adopting the servo motor unit 150, which consists of multiple ultra-low inertia servo motors connected in series, it becomes possible to control large torques that fluctuate with high angular acceleration (angular jerk), and accurately reproduce the output of automobile engines (especially the torque oscillation of reciprocating engines). Furthermore, by using the servo motor unit 150, the responsiveness of torque control is also improved, achieving a response time of 3 ms or less. A rotary drive device with such a configuration can be used as a power source for various devices, not just rotary torsion testing apparatuses. In particular, in automotive (or automotive parts) testing apparatuses, it can be used as a power simulator (simulated engine) capable of outputting power that simulates various types of engine outputs. In addition, because the torque generated by the servo motor unit 150 is controlled with high precision, it has extremely high reproducibility and no individual differences. Therefore, it is possible to apply a more uniform load than in conventional tests using actual engines, resulting in more reproducible tests.

[0055] (Modified version of the first embodiment) Figures 7 and 8 are external views of power simulators 1a and 1b, respectively, which are modified versions of the rotary torsion testing apparatus 1 according to the first embodiment of the present invention described above.

[0056] The power simulator 1a shown in Figure 7 differs from the rotational torsion testing apparatus 1 described above in that it includes a bearing section 1020, a slip ring 1401, and a mounting section 173. The bearing section 1020 has the same configuration as the bearing section 1020 of the second embodiment 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 section 1020 and extracts the signal output from the torque sensor built into the bearing section 1020 to the outside. The mounting section 173 is a flange joint and is attached to the tip of the connecting shaft 170. The power simulator 1a configured in this way is used for durability testing of engine accessories (e.g., damper pulley, alternator, balance shaft, starter motor, ring gear, water pump, oil pump, chain, timing belt, coupling, VCT), power transmission devices, tires, etc.

[0057] Furthermore, in the rotational torsion testing apparatus 1 and power simulator 1a described above, the inverter motor 80 is placed on the lower base plate 11 and the load application unit 100 is placed on the upper base plate 12, forming a two-tiered structure. However, as shown in the power simulator 1b in Figure 8, a single-tiered structure in which the inverter motor 80 and the load application unit 100 are placed on the same base plate 10X may also be used. Note that the two-tiered structure is effective in reducing the installation area. On the other hand, the single-tiered structure is advantageous in terms of cost reduction due to its simple structure, and is also advantageous in improving the rigidity of the base (i.e., vibration resistance and load-bearing characteristics).

[0058] Next, a specific example of a durability testing apparatus for engine auxiliary equipment using the power simulator 1a will be described. The test apparatus 100E described below is a test apparatus for a starter motor that performs a durability test by applying a rotational driving force that simulates the engine load generated by the power simulator 1a to the flywheel ring gear T1 and the starter motor T2, which are the test specimens. The test apparatus 100E holds the starter motor and the flywheel ring gear in an engaged state and applies the rotational driving force of the power simulator 1a to them to perform a durability test of the starter motor and the ring gear.

[0059] Figure 9 is a side view of the test apparatus 100E. Figure 10 is an enlarged view of the area around the test specimen (ring gear T1, starter motor T2).

[0060] As shown in Figures 9 and 10, the test apparatus 100E is a power simulator 1a with an added support section S for holding the test specimen. Specifically, the test apparatus 100E includes an inverter motor 80 mounted on the lower base plate 11 of the frame 10 and a load-applying section 100 rotatably supported by bearing sections 1020, 30, and 40 mounted on the upper base plate 12. The load-applying section 100 is rotationally driven by the inverter motor 80. The load-applying section 100 incorporates a servo motor unit 150 and a reduction gear, and the output shaft of the servo motor unit 150 is connected via the reduction gear to a connecting shaft 170 that protrudes from the outside of the load-applying section 100. The connecting shaft 170 is arranged coaxially with the rotation axis of the load-applying section 100, and the rotation of the connecting shaft 170 is the sum of the rotation of the load-applying section 100 by the inverter motor 80 and the rotation of the servo motor unit 150. The inverter motor 80 reproduces the engine's rotational speed, and the servo motor unit 150 reproduces the engine's high-speed fluctuating torque (high angular acceleration, high angular jerk (angular accelerometer)).

[0061] A mounting portion 173 for attaching the ring gear T1 is attached to the tip of the connecting shaft 170 of the load-applying section 100. In addition, 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 mounting portion 173 and the starter motor T2 is attached to the support portion S, the pinion gear of the ring gear T1 and the starter motor T2 engage with each other. In this state, the power simulator 1a of the test apparatus 100E is driven to apply rotation simulating engine rotation to the ring gear T1 and the starter motor T2, and the test is performed.

[0062] (Second Embodiment) Next, a power circulation type rotary torsion testing apparatus 1000 according to a second embodiment of the present invention will be described. The rotary torsion testing apparatus 1000 is a device that performs a rotary torsion test using an automobile propeller shaft as the test specimen T2, and can apply a fixed or variable torque set between the input shaft and output shaft of the propeller shaft while rotating the propeller shaft. Figure 11 is a plan view of the rotary torsion testing apparatus 1000, and Figure 12 is a side view of the rotary torsion testing apparatus 1000 (viewed from the bottom to the top in Figure 11). Figure 13 is a longitudinal cross-sectional view of the vicinity of the load application section 1100, which will be described later. The control system of the rotary torsion testing apparatus 1000 has the same schematic configuration as the first embodiment shown in Figure 6.

[0063] As shown in Figure 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, a load application unit 1100 that applies a predetermined torque between both ends of the test specimen T2 while rotating together with the test specimen T2, bearing units 1020, 1030, and 1040 that rotatably support the load application unit 1100, slip ring units 1050, 1060, and 1400 that electrically connect the wiring inside and outside the load application unit 1100, and the rotational speed of the load application unit 1100. The system includes a rotary encoder 1070 for detection, an inverter motor 1080 that rotates a load application unit 1100 and one end of the test specimen T2 (the right end in Figure 11) in a set rotational direction and speed, a drive force transmission unit 1190 (drive pulley 1191, drive belt (timing belt) 1192, and driven pulley 1193) that transmits the driving force of the inverter motor 1080 to the load application unit 1100, and a drive force transmission unit 1200 that transmits the driving force of the inverter motor 1080 to one end of the test specimen T2. ​​The drive force transmission unit 1200 includes a bearing unit 1210, a drive shaft 1212, an intermediate shaft 1220, a bearing unit 1230, a drive shaft 1232, a drive pulley 1234, a bearing unit 1240, a drive shaft 1242, a driven pulley 1244, a drive belt (timing belt) 1250, and a workpiece mounting unit 1280.

[0064] Furthermore, the bearing sections 1020, 1030, 1040, slip ring section 1050, slip ring section 1060, rotary encoder 1070, inverter motor 1080, and drive pulley 1091 in the rotary torsion testing device 1000 are configured in the same way as the bearing sections 20, 30, 40, slip ring section 50, slip ring section 60, rotary encoder 70, inverter motor 80, and drive pulley 91 in the rotary torsion testing device 1 of the first embodiment. Also, the load application section 1100 has the same configuration as the load application section 100 of the first embodiment, except for the shaft section 1120, connecting shaft 1170, workpiece mounting section 1180, and slip ring section 1400, which will be described later. In addition, the drive belt 1192 differs from the configuration of the drive belt 92 of the first embodiment in that it is worn on the driven pulley 1193 on the driven side, but its other configurations 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 components identical or similar to those in the first embodiment, and detailed explanations are omitted. The focus will be on the structural differences from the first embodiment.

[0065] The four bases 1011, 1012, 1013, and 1014 are each placed on the same flat floor F and fixed by fixing bolts (not shown). The inverter motor 1080 and the bearing section 1210 are fixed to base 1011. The bearing sections 1020, 1030, and 1040 that support the load-applying section 1100 and the support frame 1402 for the slip ring section 1400 are fixed to base 1012. The bearing section 1230 is fixed to base 1013 and the bearing section 1240 is fixed to base 1014. Bases 1013 and 1014 can be moved in the axial direction of the bearing section 1230 or 1240 according to the length of the test specimen T1 by loosening the fixing bolts.

[0066] The connecting shaft 1170 of the load-applying section 1100 protrudes outward from the tip of the shaft section 1120 (right end in Figure 13), and a workpiece mounting section (flange joint) 1180 is fixed to the tip of the connecting shaft 1170 (right end in Figure 13). A slip ring 1401 having multiple electrode rings is attached to the axial center of the portion of the connecting shaft 1170 that protrudes from the shaft section 1120.

[0067] As shown in Figure 13, the portion of the connecting shaft 1170 housed within the shaft portion 1120 has an annular constricted section 1172 with a narrow outer diameter, and a strain gauge 1174 is attached to the circumferential surface of the constricted section 1172. The connecting shaft 1170 is a cylindrical member having a hollow section (not shown) that penetrates along its central axis, and the constricted section 1172 has an insertion hole (not shown) that connects to the hollow section. The leads (not shown) of the strain gauge 1174 are passed through the aforementioned insertion hole and hollow section formed in the connecting shaft 1170 and connected to the electrode rings of the slip ring 1401. Alternatively, instead of the hollow section and insertion hole, a wiring groove extending from the constricted section 1172 to the slip ring 1401 may be provided on the circumferential surface of the connecting shaft 1170, and the leads of the strain gauge 1174 may be passed through the wiring groove and wired to the slip ring 1401.

[0068] Below the slip ring 1401, a brush section 1403 is positioned, fixed on a support frame 1402. The brush section 1403 comprises multiple brushes arranged opposite each other so as to contact each electrode ring of the slip ring 1401. The terminals of each brush are connected to a torque measuring unit 1350 (described later) by wires (not shown).

[0069] Next, the configuration of the drive force transmission unit 1200 (Figure 11) will be described. The bearing units 1210, 1230, and 1240 rotatably support the drive shafts 1212, 1232, and 1242, respectively. One end of the drive shaft 1212 (the left end in Figure 11) is connected to the drive shaft of the inverter motor 1080 via a drive pulley 1191. Also, one end of the drive shaft 1232 (the left end in Figure 11) is connected to the other end of the drive shaft 1212 (the right end in Figure 11) via a relay shaft 1220. A drive pulley 1234 is attached to the other end of the drive shaft 1232 (the right end in Figure 11), and a driven pulley 1244 is attached to one end of the drive shaft 1242 (the right end in Figure 11). A drive belt 1250 is stretched between the drive pulley 1234 and the driven pulley 1244. Furthermore, a workpiece mounting portion (flange joint) 1280 for fixing one end of the test specimen T2 is attached to the other end of the drive shaft 1242 (the left end in Figure 11).

[0070] The driving force of the inverter motor 1080 is transmitted to the workpiece mounting section 1280 via the aforementioned drive force transmission section 1200 (i.e., drive shaft 1212, relay shaft 1220, drive shaft 1232, drive pulley 1234, drive belt 1250, driven pulley 1244, and drive shaft 1242), causing the workpiece mounting section 1280 to rotate in the set rotation direction and speed. At the same time, the driving force of the inverter motor 1080 is also transmitted to the load application section 1100 via the drive force transmission section 1190 (i.e., drive pulley 1191, drive belt 1192, and driven pulley 1193), causing the load application section 1100 and the workpiece mounting section 1280 to rotate synchronously (i.e., always at the same speed and in the same phase).

[0071] (Third embodiment) In the second embodiment described above, the drive shafts 1212 and load-applying section 1100, and the drive shafts 1232 and 1242, which are arranged parallel to each other, are connected by drive belts 1192 and 1250, respectively, to form a power circulation system. However, the present invention is not limited to this configuration, and configurations in which power is transmitted using a gear system instead of a drive belt, as in the third to seventh embodiments described below, are also included in the scope of the present invention.

[0072] Figure 14(a) is a top view of a torsion testing apparatus according to a third embodiment of the present invention. Figure 14(b) is a side view of the torsion testing apparatus according to this embodiment. As shown in Figure 14, the torsion testing apparatus 100 of this embodiment has a configuration in which a workpiece rotation servo motor 121, a torque application unit 130, a first gearbox 141, and a second gearbox 142 are fixed on a base 110.

[0073] The first gearbox 141 has four shaft connections: 141a1, 141a2, 141b1, and 141b2. The second gearbox 142 has two shaft connections: 142a and 142b.

[0074] A drive pulley 122 is attached to the output shaft 121a of the workpiece rotation servo motor 121. The shaft 123a of the driven pulley 123 is attached to the shaft connection portion 141a1 of the first gearbox 141. An endless belt 124 is stretched over the drive pulley 122 and the driven pulley 123, and by driving the workpiece rotation servo motor 121, the driven pulley 123 can be rotated at a desired rotational speed.

[0075] Torque-applying units 130 are connected to shaft connection parts 141b1 and 141b2. The configuration of the torque-applying units 130 is described below.

[0076] Figure 15 is a side cross-sectional view of the torque application unit 130 and the first gearbox 141 of this embodiment. The torque application unit 130 comprises a casing 131 and a torque application servo motor unit 132 and a reduction gear 133 fixed inside the casing 131. The torque application servo motor unit 132 has the same configuration as the servo motor unit 150 of the first embodiment, but the servo motor 150B of the first embodiment may be used alone instead of the servo motor unit 150. A tubular portion 131a is formed on one axial end (right side in the figure) of the casing 131. The tubular portion 131a is inserted into the first gearbox 141 via an axial connection portion 141b1 and is rotatably supported inside the first gearbox 141. A gear 141b3 is mounted on the tubular portion 131a.

[0077] The gearbox 133 has an input shaft 133a and an output shaft 133b, and reduces the rotational motion input to the input shaft 133a before outputting it to the output shaft 133b. The input shaft 133a of the gearbox 133 is connected to the output shaft 132a of the torque-applying servo motor unit 132 by a coupling 134. The output shaft 133b of the gearbox 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 gearbox 133 protruding from the tubular portion 131a is connected to the shaft connection portion 141b2 of the first gearbox 141.

[0078] As shown in Figure 14, the output shaft 133b of the reduction gear 133 is connected to the input shaft W1a of the transmission unit W1 under test via a coupling 151. The output shaft W1b of the transmission unit W1 is connected to the shaft connection portion 142b of the second gearbox 142 via a torque sensor 160.

[0079] The output shaft W2b of the transmission unit W2 is connected to the shaft connection portion 142a of the second gearbox 142 via a relay shaft 143. The input shaft W2a of the transmission unit W2 is connected to the shaft connection portion 141a2 of the first gearbox 141 via a coupling 152.

[0080] Here, the shaft 123a of the driven pulley 123 mounted on the shaft connection portion 141a1 of the first gearbox 141 and the shaft mounted on the shaft connection portion 141a2 are connected inside the first gearbox 141 via a coupling 153, and are configured to rotate together as a single unit. A gear 141a3 is mounted on the shaft 123a of the driven pulley 123 mounted on the shaft connection portion 141a1. A gear 141b3 is mounted inside the first gearbox 141 on the tubular portion 131a connected to the shaft connection portion 141b1. As shown in Figure 14(a), gears 141a3 and 141b3 mesh via an intermediate gear 141i, and rotational motion can be transmitted between the shafts connected to the shaft connection portions 141a1 and 141a2 and the shaft connected to the shaft connection portion 141b1. Furthermore, since the intermediate gear 141i is interposed between gear 141a3 and gear 141b3, the driven pulley 123, the intermediate shaft 143, and the casing 131 of the torque application unit 130 rotate in the same direction.

[0081] A gear 142a1 is mounted on the shaft (one end of the intermediate shaft 143) connected to the shaft connection part 142a. A gear 142b1 is connected to the shaft connected to the shaft connection part 142b. Gears 142a1 and 142b1 mesh within the second gearbox 142 via an intermediate gear 142i, enabling the transmission of rotational motion between the shaft connected to shaft connection part 142a and the shaft connected to shaft connection part 142b. Since the intermediate gear 142i is interposed between gears 142a1 and 142b1, the shaft connected to shaft connection part 142a and the shaft connected to shaft connection part 142b rotate in the same direction.

[0082] Therefore, in this embodiment, when the workpiece rotation servo motor 121 (Figure 14) is driven, the driven pulley 123 and the casing 131 (Figure 15), which is connected to the driven pulley 123 via gears, are rotated. As mentioned above, since the torque-applying servo motor unit 132 is fixed to the casing 131, the casing 131 and the torque-applying servo motor rotate together. Therefore, when the torque-applying servo motor unit 132 is driven while the casing 131 is rotating, the output shaft 133b of the reduction gear 133 rotates at a rotational speed that is the sum of the rotational speed of the casing 131 and the rotational speed of the output shaft 133b by the torque-applying servo motor unit 132.

[0083] Transmission unit W2 is identical to transmission unit W1 (same reduction ratio). Furthermore, the gear ratios of gearboxes 141 and 142 are both 1:1. Therefore, the rotational speeds of the shafts connected to shaft connection points 141a2 and 141b2 of the first gearbox 141 are approximately equal. Note that transmission unit W2 is a kind of dummy workpiece used to equalize the rotational speeds of the shafts connected to shaft connection points 141a2 and 141b2, as described above, and is not subject to torsional testing.

[0084] In this embodiment, for example, by driving the workpiece rotation servo motor 121 at a constant speed and driving the output shaft 132a reciprocatingly with the torque application servo motor unit 132 (Figure 15), it becomes possible to apply periodically fluctuating torque while rotating the input shaft W1a of the transmission unit W1.

[0085] (Fourth Embodiment) Next, a fourth embodiment of the present invention will be described. Figure 16 is a top view of a torsion testing apparatus according to the fourth embodiment of the present invention. As shown in Figure 16, the torsion testing apparatus 100A of this embodiment is identical to the torsion testing apparatus 100 of the third embodiment, except that it does not use a dummy workpiece and the shaft connection portion 142a of the coupling 152 and the second gearbox 142 is directly connected by an intermediate shaft 143A. In the following description of the fourth embodiment, elements having the same or similar functions as those of the third embodiment will be denoted by the same or similar reference numerals, and redundant explanations will be omitted.

[0086] In this embodiment, the rotational speed of the relay shaft 143A (i.e., the rotational speed of the casing 131 of the torque application unit 130) and the rotational speed of the shaft connected to the shaft connection portion 141b2 of the first gearbox 141 (i.e., the rotational speed of the input shaft W1a of the transmission unit W1) are different. Therefore, in this embodiment, the torque application servo motor unit 132 (Figure 15) of the torque application unit 130 is rotationally driven to compensate for the change in rotational speed at the input and output shafts of the transmission unit W1. For example, if the reduction ratio of the transmission unit W1 is 1 / 3.5, and a torsional test is performed with the input shaft W1a rotating at 4000 rpm and the output shaft W1b rotating at 1143 rpm, the rotation speed of the workpiece rotation servo motor 121 is set to apply a rotation of 1143 rpm to the casing 131 of the torque application unit 130. At the same time, the rotation speed of the torque application servo motor 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. In this way, the rotation speed of the input shaft W1a of the transmission unit W1 can be set to 4000 rpm.

[0087] Thus, in this embodiment, a torsional test of the transmission unit W1 can be performed while circulating power without using a dummy workpiece.

[0088] Furthermore, in this embodiment, since the rotational drive of the workpiece and torque application are performed by a highly responsive servo motor, it is possible to change the gear ratio of the transmission unit W1 while the torsional test is being performed. In other words, in this embodiment, it is possible to rapidly change the rotational speed of the torque application servo motor unit 131 in synchronization with the change in rotational speed of the output shaft W1b due to the change in the gear ratio of the transmission unit W1. Therefore, even if the gear ratio of the transmission unit W1 is changed, excessive load will not be placed on the gears in the gearboxes 141 and 142 or the transmission unit W1, preventing damage.

[0089] (Fifth embodiment) In the third and fourth embodiments of the present invention, a transmission unit is used as the test subject (workpiece). However, the present invention is not limited to the above configuration, and it is also possible to perform torsional testing on other types of workpieces. The torsional testing apparatus according to the fifth embodiment of the present invention, described below, performs torsional testing on the entire power transmission system of a rear-wheel-drive vehicle as the workpiece.

[0090] Figure 17 is a top view of a torsion testing apparatus according to a fifth embodiment of the present invention. As shown in Figure 17, the torsion testing apparatus 100B according to this embodiment performs a torsion test on the power transmission system W3 of an FR vehicle, which consists of a transmission unit TR1, a propeller shaft PS, and a differential gear DG1.

[0091] In this embodiment, the torsion testing apparatus 100B has two output shafts (DG1a and DG1b) for the differential gear DG1, and therefore has two second gearboxes (142B1 and 142B2) and two intermediate shafts (143B1 and 143B2) to return the output of the differential gear DG1 to the first gearbox 141B. Specifically, the output shafts DG1a and DG1b of the differential gear DG1 are connected to the intermediate shafts 143B1 and 143B2, respectively, via the second gearboxes 142B1 and 142B2.

[0092] Furthermore, the first gearbox 141B has shaft connection parts 141Bb1 and 141Bb2 (with the same function as shaft connection parts 141b1 and 141b2 of the third embodiment) to which the tubular portion 131a of the casing 131 of the torque application unit 130 and the input shaft TR1a of the transmission unit TR1 are attached, respectively, as well as shaft connection parts 141Ba1 and 141Ba2 to which the output shaft 121a of the workpiece rotation servo motor 121 and the intermediate shaft 143B1 are connected, and a shaft connection part 143Bc to which the intermediate shaft 143B2 is connected. In addition, the output shaft 121a of the workpiece rotation servo motor 121 and the intermediate shaft 143B1 are connected via a coupling 153B located inside the first gearbox 141. Furthermore, the input shaft TR1a of the transmission unit TR1 and the output shaft 133b of the reduction gear 133 of the torque application unit 130 are connected via a coupling 151B located inside the first gearbox 141.

[0093] The shafts connected to the shaft connection sections 141Ba1, 141Bb1, and 141Bc are connected to each other via gears and intermediate gears (not shown) that are separately attached to each shaft. When the workpiece rotation servo motor 121 is driven, the relay shafts 143B1 and 143B2 and the casing 131 of the torque application unit 130 rotate.

[0094] In this embodiment, as in the fourth embodiment, the rotational speed of the input shaft TR1a of the transmission unit TR1 and the rotational speeds of the intermediate shafts 143B1 and 143B2 are different. Therefore, the rotational speed of the torque-applying motor 131 (Figure 15) is controlled to compensate for the difference in rotational speeds.

[0095] (Sixth Embodiment) Furthermore, in the configuration of the present invention, it is also possible to use a power transmission system for a front-wheel-drive (FF) vehicle as the workpiece. The torsional testing apparatus according to the sixth embodiment of the present invention, described below, performs a torsional test on the power transmission system of an FF vehicle.

[0096] Figure 18 is a top view of the torsion testing apparatus 100C according to the sixth embodiment of the present invention. As shown in Figure 18, the torsion testing apparatus 100C of this embodiment performs a torsion test on a power transmission system W4 for a front-wheel-drive vehicle, which is an integrated transmission unit TR2 with a built-in torque converter TC and a differential gear DG2.

[0097] As shown in Figure 18, the power transmission system W4 is a power transmission system for a transversely mounted 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 to each other. 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.

[0098] The first gearbox 141C of this embodiment, like the fifth embodiment, has shaft connection parts 141Cb1 and 141Cb2 to which the tubular portion 131a of the casing 131 of the torque application unit 130 and the input shaft TR2a of the transmission unit TR2 are attached, respectively; shaft connection parts 141Ca1 and 141Ca2 to which the output shaft 121a of the workpiece rotation servo motor 121 and the output shaft DG2a of the differential gear DG2 are connected; and shaft connection part 143Cc to which the intermediate shaft 143C is connected. The output shaft 121a of the workpiece rotation servo motor 121 and the output shaft DG2a of the differential gear DG2 are connected by a coupling 153C located inside the first gearbox 141C. In addition, the output shaft 133b of the reduction gear 133 of the torque application unit 130 and the input shaft TR2a of the transmission unit TR2 are connected by a coupling 151C located inside the first gearbox 141C.

[0099] The shafts connected to the shaft connection sections 141Ca1, 141Cb1, and 141Cc are connected to each other via gears that are separately attached to each shaft. When the workpiece rotation servo motor 121 is driven, the output shaft DG2a of the differential gear DG2, the intermediate shaft 143C, and the casing 131 of the torque application unit 130 rotate.

[0100] Furthermore, in this embodiment, as in the fourth and fifth embodiments, the rotational speed of the input shaft TR2a of the transmission unit TR2 and the rotational speed of the output shaft DG2a and intermediate shaft 143C of the differential gear DG2 are different. Therefore, the rotational speed of the torque-applying motor 131 (Figure 15) is controlled to compensate for the difference in rotational speeds.

[0101] (Seventh Embodiment) Figure 19 is an external view of the rotational torsion testing apparatus 100B according to the seventh embodiment of the present invention. As shown in Figure 19, the torsion testing apparatus 100B according to this embodiment performs a rotational torsion test on the differential gear DG1.

[0102] In this embodiment, the torsion testing apparatus 100B has two output shafts (DG1a and DG1b) for the differential gear DG1. Therefore, two second gearboxes (142B1 and 142B2), two bevel gearboxes (144B1 and 144B2), and two intermediate shafts (143B1 and 143B2) are provided to return the output of the differential gear DG1 to the first gearbox 141B. Specifically, the output shafts DG1a and DG1b of the differential gear DG1 are connected to the intermediate shafts 143B1 and 143B2, respectively, via the second gearboxes 142B1 and 142B2 and the bevel gearboxes 144B1 and 144B2.

[0103] The first gearbox 141B also includes a gear 141Bb and gears 141Ba and 141Bc that engage with gear 141Bb, respectively. The tubular portion of the casing of the torque-applying unit 130 is connected to gear 141Bb. The intermediate shafts 143B1 and 143B2 are connected to gears 141Ba and 141Bc, respectively. As a result, when the inverter motor 80 is driven, the intermediate shafts 143B1 and 143B2 and the casing 131 of the torque-applying unit 130 rotate.

[0104] The output shafts DG1a, DG1b and input shaft DG1c of the differential gear DG1 are connected to the shafts of the respective gearboxes 142B1, 142B2 and torque application unit 130 via torque sensors 172a, 172b, and 172c, respectively. The torque sensors 172a, 172b, and 172c are configured such that a shaft 1170 with a strain gauge 1174 attached to a constricted portion 1172 is supported by a bearing portion 1020 (directly without going through the shaft portion 1120), as shown in Figure 13 (second embodiment).

[0105] In this embodiment, since the rotational speed of the input shaft DG1c of the differential gear DG1 differs from the rotational speeds of the output shafts DG1a and DG1b, the rotational speed of the servo motor unit 150 built into the torque application unit 130 is controlled to compensate for this difference in rotational speed.

[0106] (Eighth embodiment) Furthermore, the present invention can also be applied to a test apparatus for power transmission systems of FF vehicles. The torsional testing apparatus according to the eighth embodiment of the present invention, described below, is a power circulation type test apparatus for performing rotational torsional testing on the power transmission system of an FF vehicle.

[0107] Figure 20 is an external view of the torsion testing apparatus 100C according to the eighth embodiment of the present invention. As shown in Figure 20, the torsion testing apparatus 100C of this embodiment performs rotational torsion testing on a transmission unit TR for a front-wheel-drive vehicle.

[0108] As shown in Figure 20, the input shaft TRa and output shafts TRb and TRc of the transmission unit TR are all connected to the first gearbox 141C via torque sensors 172b, 172b, and 172c, respectively, without any reduction in speed. Furthermore, the input shaft TRa and output shafts TRb and TRc of the transmission unit TR are arranged substantially parallel to each other. Therefore, in this embodiment, the input shaft TRa and one of the output shafts TRb of the transmission unit TR are directly connected to the first gearbox 141C, while the other output shaft TRc is connected to the first gearbox 141C via the second gearbox 142C and a relay shaft 143C that is arranged substantially parallel to the output shaft TRc. In other words, the driving force of the output shaft TRc is reflected 180° by the second gearbox 142C and then transmitted to the first gearbox 141C by the relay shaft 143C.

[0109] The first gearbox 141C of this embodiment includes a gear 141Cb and gears 141Ca and 141Cc that engage with gear 141Cb, respectively. Gear 141Ca engages with gear 141Cb via a pinion gear, and the rotation of gear 141Cb is reduced and transmitted to gear 141Ca. The tubular portion of the casing of the torque application unit 130 is connected to gear 141Ca, and the output shaft of the inverter motor 80 is connected to gear 141Cc via a timing belt. As a result, when the inverter motor 80 is driven, the output shaft TRb of the lance transmission unit TR, the output shaft TRc (via the relay shaft 143C), and the casing of the torque application unit 130 rotate.

[0110] Furthermore, in this embodiment, since the transmission unit TR has a reduction ratio, the rotational speed of the input shaft TRa is different from the rotational speeds of the output shafts TRb and TRc. Therefore, the rotational speed of the servo motor unit 150 built into the torque application unit 130 is controlled to compensate for this difference in rotational speed.

[0111] The third to eighth embodiments of the present invention described above are examples of applying the present invention to a power circulation type torsion testing apparatus using a power transmission system such as a transmission unit as the workpiece. However, the present invention is not limited to the above configuration. As shown in the ninth and tenth embodiments of the present invention described below, it is also possible to apply the present invention to various tire tests.

[0112] (Ninth Embodiment) Figure 21 is a top view of a tire wear testing apparatus 100D according to the ninth embodiment of the present invention. The tire wear testing apparatus 100D has a power circulation mechanism with the same configuration as that of the third embodiment described above.

[0113] The first gearbox 141D has four shaft connections: 141Da1, 141Da2, 141Db1, and 141Db2. The second gearbox 142D has two shaft connections: 142Da and 142Db.

[0114] In this embodiment, both ends of the shaft 145, which serves as the rotation axis of the rotating drum DR acting as a simulated road surface, are connected to the shaft connection portion 141Da2 of the first gearbox 141D and the shaft connection portion 142Da of the second gearbox 142D, respectively. In addition, both ends of the shaft 144, which serves as the rotation axis of the tire T being tested, are connected to the shaft connection portion 141Db2 of the first gearbox 141D and the shaft connection portion 142Db of the second gearbox 142D, respectively.

[0115] Similar to the second embodiment, the rotation of the output shaft 121a of the workpiece rotation servo motor 121 for driving the tire T and the rotating drum DR is configured to rotate the shaft 123a of the driven pulley 123 via a belt mechanism consisting of a drive pulley 122, a driven pulley 123, and an endless belt 124. The shaft 123a is connected to the shaft connection portion 141a of the first gearbox 141D.

[0116] The tubular portion 131a of the casing 131 of the torque application unit 130 is connected to the shaft connection portion 141Db1 of the first gearbox 141D. In addition, the output shaft 133b of the reduction gear 133 of the torque application unit 130 is connected to one end of the shaft 144 for the tire T via a coupling 151D located inside the first gearbox 141D.

[0117] One end of the shaft 145 for the rotating drum DR, which is attached to the first gearbox 141D, is connected to the shaft 123a of the driven pulley 123 via a coupling 153D located inside the first gearbox 141D.

[0118] The shaft 123a mounted on the shaft connection portion 141Da1 of the first gearbox 141D and the shaft (tubular portion 131a) mounted on the shaft connection portion 141Db1 are each connected to different gears provided inside the first gearbox 141. These gears mesh with each other inside the second gearbox 142, and when the workpiece rotation servo motor 121 is driven, the shaft 145 for the rotating drum DR and the casing 131 of the torque application unit 130 rotate.

[0119] Furthermore, the shaft 145 mounted on the shaft connection portion 142Da of the second gearbox 142 and the shaft 144 mounted on the shaft connection portion 142Db are each connected to different gears provided inside the second gearbox 142. These gears mesh with each other inside the second gearbox 142, and the rotation of shaft 144 is transmitted to shaft 145 by the second gearbox 142.

[0120] As described above, the rotating servo motor 121 is driven to rotate the rotating drum DR and the tire T while circulating power. As shown in Figure 21, in this embodiment, the diameters of the rotating drum DR and the tire T are different, so the gear ratios in the first gearbox 141D and the second gearbox 142D are set to values ​​corresponding to the ratio of the diameters of the rotating drum DR and the tire T.

[0121] In the tire wear testing apparatus with the configuration described above, the tire T and the rotating drum DR rotate by setting the tire T on the shaft 144 and driving the rotation servo motor 121. In this state, by driving the torque application servo motor unit 131 (Figure 2) of the torque application unit 130 and applying torque in the forward or reverse direction to the tire T, it becomes possible to perform a wear test that simulates the acceleration and deceleration of an automobile.

[0122] (Tenth embodiment) Here is another example of an application of the present invention to tire testing. The tire testing apparatus according to the 10th embodiment of the present invention, described below, is a testing apparatus for performing tire wear tests, durability tests, driving stability tests, and the like.

[0123] Figures 22 and 23 are perspective views of the tire testing apparatus 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 on which a simulated road surface is formed on its outer circumference, an inverter motor 80 that rotationally drives the casing of the rotating drum 10 and the torque application unit 130, an alignment control mechanism 160, and a torque application unit 130 that applies torque to a tire T rotatably supported by the alignment control mechanism 160. The torque application unit 130 incorporates a servo motor unit 150 with the same configuration as that of the first embodiment.

[0124] The rotating drum 10 is rotatably supported by a pair of bearings 11a. A pulley 12a is attached to the output shaft of the inverter motor 80, and a pulley 12b is attached to one shaft of the rotating drum 10. Pulleys 12a and 12b are connected by a drive belt. A pulley 12c is attached to the other shaft of the rotating drum 10 via an intermediate shaft 13. The intermediate shaft 13 is rotatably supported by a bearing 11b near one end where the pulley is attached. Pulley 12c is connected to pulley 12d by a drive belt. Pulley 12d is fixed coaxially to pulley 12e and is rotatably supported together with pulley 12e by a bearing 11c (Figure 27). Furthermore, pulley 12e is connected by a drive belt to the tubular part of the casing of the torque application unit 130.

[0125] Furthermore, the drive shaft of the servo motor unit 150 built into the torque application unit 130 is connected to the wheel of the alignment control mechanism 160 on which the tire T is mounted, via the relay shaft 14 and a flexible coupling.

[0126] As a result, when the inverter motor 80 is driven, the rotating drum 10 rotates, and the casing of the torque application unit 130, which is connected to the inverter motor 80 via the rotating drum 10, also rotates. Furthermore, the rotating drum 10 and the tire T rotate in opposite directions so that their peripheral speeds at the contact point are the same when the torque application unit 130 is not operating. Additionally, by operating the torque application unit 130, dynamic driving and braking forces can be applied to the tire T.

[0127] The alignment control mechanism 160 of this embodiment supports the tire T, which is a test specimen, while it is mounted on a wheel, presses the tread portion against the simulated road surface of the rotating drum 10, and adjusts the alignment of the tire T and the tire load (ground pressure) with respect to the simulated road surface to a set state. The alignment control mechanism 160 includes a tire load adjustment unit 161 that adjusts the tire load by moving the position of the rotation axis of the tire T in the radial direction of the rotating drum 10, a slip angle adjustment unit 162 that adjusts the slip angle of the tire T with respect to the simulated road surface by tilting the rotation axis of the tire T around a perpendicular 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 a traverse device 164 that moves the tire T in the rotation axis direction.

[0128] By setting a tire T in the tire testing apparatus 100D with the configuration described above and driving the inverter motor 80 for rotational drive, the tire T and the rotating drum 10 rotate at the same peripheral speed. In this state, by driving the servo motor unit 150 of the torque application unit 130 to apply driving force and braking force to the tire T, it becomes possible to perform tire wear tests, durability tests, driving stability tests, etc., that simulate actual driving conditions.

[0129] (11th 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.

[0130] Figure 24 is an external view of the power absorption type durability testing apparatus 100F for an FR transmission according to the 11th embodiment of the present invention.

[0131] The test apparatus 100F includes a power simulator 100X equipped with an inverter motor 80 and a load application unit 100 incorporating a servo motor unit 150, a support unit S for supporting the case of the FR transmission T which is the test specimen, torque sensors 172a and 172b, and two power absorption servo motors 90A and 90B. The input shaft of the FR transmission T is connected to the output shaft of the load application unit 100 via the torque sensor 172a. The output shaft To of the FR transmission T is connected to the pulley unit 180 via the torque sensor 172b. The torque sensors 172a and 172b have the same configuration as the torque sensors 172a, 172b, and 172c of the seventh embodiment.

[0132] The pulley section 180 is connected to two power absorption servo motors 90A and 90B by two drive belts. The two power absorption servo motors 90A and 90B are driven synchronously to apply a load to the output shaft To of the FR transmission T.

[0133] (12th embodiment) Figure 25 is an external view of the power absorption type durability testing apparatus 100G for an FF transmission according to the 12th embodiment of the present invention.

[0134] The test specimen, the FF transmission TR, comprises one input shaft and two output shafts TRb and TRc. The input shaft of the FF transmission TR is connected to the output shaft of the load application unit 100 via a torque sensor 172a. The output shafts TRb (TRc) of the FF transmission TR are connected to a power absorption servo motor 90B (90C) via a torque sensor 172b (172c), a pulley unit 180b (180c), and a drive belt. The power absorption servo motor 90B (90C) applies a load to the output shafts TRb (TRc) of the FF transmission TR. The torque sensors 172a, 172b, and 172c have the same configuration as those in the seventh embodiment.

[0135] (13th Embodiment) Next, a low-speed rotary torsion testing apparatus according to the 13th embodiment of the present invention will be described. Figure 26 is a side view of the torsion testing apparatus 3100 according to the 13th embodiment of the present invention. The torsion testing apparatus 3100 of this embodiment is a device for performing a rotary torsion test on a test specimen T1 (for example, a transmission unit for a front-engine, rear-wheel-drive vehicle) having two rotating shafts. That is, the torsion testing apparatus 3100 rotates the two rotating shafts of the test specimen T1 while applying a phase difference to the rotation of the two rotating shafts, thereby applying torque to rotate the two rotating shafts of the test specimen T1. The torsion testing apparatus 3100 of this embodiment includes a first drive unit 3110, a second drive unit 3120, and a control unit C3 that integrally controls the operation of the torsion testing apparatus 3100.

[0136] First, the structure of the first drive unit 3110 will be described. Figure 27 is a cutaway side view of the first drive unit 3110. The first drive unit 3110 comprises a main body 3110a and a base 3110b that supports the main body 3110a at a predetermined height. The main body 3110a comprises a servo motor unit 150, a reducer 3113, a case 3114, a spindle 3115, a chuck device 3116, a torque sensor 3117, a slip ring 3119a, and a brush 3119b. The main body 3110a is assembled on a movable plate 3111 which is horizontally positioned at the top of the base 3110b. The 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) facing horizontally. Furthermore, the movable plate 3111 of the base 3110b is provided so as to be slidable in the output axis direction (left-right direction in Figure 26) of the servo motor unit 150.

[0137] The output shaft (not shown) of the servo motor unit 150 is connected to the input shaft (not shown) of the reduction gear 3113 by a coupling (not shown). The output shaft 3113a of the reduction gear 3113 is connected to one end of the torque sensor 3117. The other end of the torque sensor 3117 is connected to one end of the spindle 3115. The spindle 3115 is rotatably supported by a bearing 3114a fixed to the frame 3114b of the case 3114. A chuck device 3116 for attaching one end (one of the rotation axes) of the test specimen T1 to the first drive unit 3110 is fixed to the other end of the spindle 3115. When the servo motor unit 150 is driven, the rotational motion of the output shaft of the servo motor unit 150 is reduced by the reduction gear 113 and then transmitted to one end of the test specimen T1 via the torque sensor 3117, spindle 3115 and chuck device 3116. Furthermore, a rotary encoder (not shown) is attached to the spindle 3115 to detect the rotation angle of the spindle 3115.

[0138] As shown in Figure 27, the reducer 3113 is fixed to the frame 3114b of the case 3114. The reducer 3113 also comprises a gear case and a gear mechanism (not shown) rotatably supported by the gear case via bearings. In other words, the case 3114 covers the power transmission shaft from the reducer 3113 to the chuck device 3116, and also functions as a device frame that rotatably supports this power transmission shaft at the positions of the reducer 3113 and the spindle 3115. Specifically, the gear mechanism of the 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 rotatably supported by the frame 3114b of the case 3114 via bearings. Therefore, the torque sensor 3117 is not subjected to bending moments caused by the gear mechanism of the reducer 3113 or the weight of the spindle 3115 (and chuck device 3116), and only the test load (torsional load) is applied, allowing for highly accurate detection of the test load.

[0139] Multiple slip rings 3119a are formed on the cylindrical surface at one end of the torque sensor 3117. Meanwhile, a brush holding frame 3119c is fixed to the movable plate 3111 so as to surround the slip rings 3119a from the outer circumference. Multiple brushes 3119b are attached to the inner circumference of the brush holding frame 3119c, each corresponding to a slip ring 3119a that contacts the slip ring. When the servo motor unit 150 is driven and the torque sensor 3117 is rotating, the brushes 3119b slip on the slip rings 3119a while maintaining contact with them. The output signal of the torque sensor 3117 is configured to be output to the slip rings 3119a, and the output signal of the torque sensor 3117 can be taken out to the outside of the first drive unit 3110 via the brushes 3119b that contact the slip rings 3119a.

[0140] The second drive unit 3120 (Figure 26) has the same structure as the first drive unit 3110, and when the servo motor unit 150 is driven, the chuck device 3126 rotates. The other end (one of the rotation axes) of the test specimen T1 is fixed to the chuck device 3126. The housing of the test specimen T1 is fixed to the support frame S.

[0141] The torsion testing apparatus 3100 of this embodiment fixes the output shaft O and input shaft I (engine side) of the test specimen T1, which is a transmission unit for a rear-wheel-drive vehicle, to the chuck devices 3116 and 3126 of the first drive unit 3110 and the second drive unit 3120, respectively, and rotates them synchronously using servo motor units 150, 150. A torsional load is applied to the test specimen T1 by creating a difference in the rotational speed (or rotational phase) of the two chuck devices 3116 and 3126. 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 rotated so that the torque detected by the torque sensor 3117 of the first drive unit 3110 fluctuates according to a predetermined waveform, thereby applying a periodically fluctuating torque to the test specimen T1, which is a transmission unit.

[0142] Thus, the torsion testing apparatus 3100 of this embodiment can precisely drive both the input shaft I and the output shaft O of the transmission unit with servo motor units 150, 150. Therefore, by applying fluctuating torque to each shaft of the transmission unit while rotating the transmission unit, the test can be performed under conditions close to the actual driving conditions of an automobile.

[0143] When performing a rotational torsion test on a device such as a transmission unit, where the input shaft I and output shaft O are connected via gears or the like, the magnitude of the torque applied to the input shaft I and output shaft O does not necessarily coincide. Therefore, in order to more accurately understand the behavior of the test specimen T1 during the torsion test, it is preferable to be able to measure the torque separately on the input shaft I side and the output shaft O side. In this embodiment, as described above, torque sensors are provided on both the first drive unit 3110 and the second drive unit 3120, so that the torque can be measured separately on the input shaft I side and the output shaft O side of the transmission unit (test specimen T1).

[0144] In the above example, the input shaft I of the transmission unit is driven at a constant speed, and torque is applied to the output shaft O. However, the present invention is not limited to the above example. That is, the output shaft O of the transmission unit may be driven at a constant speed, while a variable torque is applied to the input shaft I. Alternatively, both the input shaft I and the output shaft O of the transmission unit may be driven at varying rotational speeds. Furthermore, the torque of each shaft may be controlled without controlling the rotational speed. Also, the torque and rotational speed may be varied according to a predetermined waveform. The torque and rotational speed can be varied according to an arbitrary waveform generated, for example, by a function generator. Furthermore, the torque and rotational speed of each shaft of the test specimen T1 can be controlled based on waveform data of torque and rotational speed measured in actual driving tests.

[0145] The torsion testing apparatus 3100 of this embodiment is designed to accommodate transmission units of various dimensions, with adjustable spacing between the chuck devices 3116 and 3126. Specifically, a movable plate drive mechanism (not shown) allows the movable plate 3111 of the first drive unit 3110 to move relative to the base 3110b in the direction of rotation of the chuck device 3116 (left-right direction in Figure 26). During the rotational torsion test, the movable plate 3111 is firmly fixed to the base 3110b by a locking mechanism (not shown). The second drive unit 3120 also has a movable plate drive mechanism similar to that of the first drive unit 3110.

[0146] The torsion testing apparatus 3100 according to the 13th embodiment of the present invention described above is used to perform rotational torsion tests on transmission units for FR vehicles. However, the present invention is not limited to the configuration of the basic example of the 13th embodiment described above, and apparatuses for performing rotational torsion tests on other power transmission mechanisms are also included in the present invention. The first, second, and third modifications of the 13th embodiment of the present invention described below are examples of torsion testing apparatus configurations suitable for testing transmission units for FF vehicles, differential gear units, and transmission units for 4WD vehicles, respectively.

[0147] (First modified example of the 13th embodiment) Figure 28 is a plan view of a torsion testing apparatus 3200 according to the first modified example of the 13th embodiment of the present invention. As described above, this modified example is a configuration example of a torsion testing apparatus suitable for rotational torsion testing using a transmission unit for a front-wheel-drive vehicle as the test specimen T2. ​​The test specimen T2 is a transmission unit that incorporates a differential gear and has an input shaft I, a left output shaft OL, and a right output shaft OR.

[0148] The torsion testing apparatus 3200 of this modified example includes a first drive unit 3210 that drives the input shaft I of the test specimen T2, a second drive unit 3220 that drives the left output shaft OL, and a third drive unit 3230 that drives the right output shaft OR. The torsion testing apparatus 3200 also includes a control unit C3a that comprehensively controls its operation. The structures of the first drive unit 3210, the second drive unit 3220, and the third drive unit 3230 are all the same as those of the first drive unit 3110 and the second drive unit 3120 in the basic example of the 13th embodiment described above, so a redundant explanation of the specific configuration will be omitted.

[0149] When performing a rotational torsion test on a specimen T2 using the torsion testing apparatus 3200 of this modified example, for example, the input shaft I is driven at a predetermined rotational speed by the first drive unit 3210, and at the same time, the left output shaft OL and the right output shaft OR are rotationally driven by the second drive unit 3220 and the third drive unit 3230 so as to apply a predetermined torque.

[0150] By controlling the first drive unit 3210, the second drive unit 3220, and the third drive unit 3230 as described above, the transmission unit is rotationally driven while fluctuating torque is applied to each shaft of the transmission unit, allowing the test to be conducted under conditions close to the actual driving conditions of an automobile.

[0151] Furthermore, the transmission unit tested using the torsion testing apparatus 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 performing a rotational torsion test on this device, the magnitudes of the torque applied to the input shaft I, the left output shaft OL, and the right output shaft OR do not coincide. Also, the torques applied to the left output shaft OL and the right output shaft OR do not necessarily coincide. Therefore, in order to more accurately understand the behavior of the test specimen T2 during the torsion test, it is preferable to be able to measure the torque applied to the input shaft I, the left output shaft OL, and the right output shaft OR individually. In this modified example, since torque sensors are provided in all of the first drive unit 3210, the second drive unit 3220, and the third drive unit 3230, the torque applied to the input shaft I, the left output shaft OL, and the right output shaft OR of the transmission unit (test specimen T2) can be measured individually.

[0152] Furthermore, the second drive unit 3220 and the third drive unit 3230 may be controlled so that the torque of the left output shaft OL and the torque of the right output shaft OR trace the same waveform, or the first drive unit 3210, the second drive unit 3220, and the third drive unit 3230 may be controlled so that they trace different waveforms (for example, out of phase).

[0153] Alternatively, the left output shaft OL and the right output shaft OR may be driven at a constant speed, and the input shaft I may be driven so that its speed fluctuates at a constant period. Or, the input shaft I, the left output shaft OL, and the right output shaft OR may all be driven so that their rotational speeds fluctuate individually.

[0154] (Second modified example of the 13th embodiment) Next, a second modification of the thirteenth embodiment of the present invention will be described. Figure 19 is a plan view of the torsion testing apparatus 3300 according to this modification. This modification is an example of the configuration of a torsion testing apparatus suitable for rotational torsion testing using a differential gear unit for a front-engine, rear-wheel-drive vehicle as the test specimen T3. Similar to the first modification, the test specimen T3 has an input shaft I, a left output shaft OL, and a right output shaft OR.

[0155] The torsion testing apparatus 3300 of this modified example includes a first drive unit 3310 that drives the input shaft I of the test specimen T3, a second drive unit 3320 that drives the left output shaft OL, and a third drive unit 3330 that drives the right output shaft OR. The torsion testing apparatus 3300 also includes a control unit C3b that comprehensively controls its operation. The structures of the first drive unit 3310, the second drive unit 3320, and the third drive unit 3330 are all the same as those of the first drive unit 3110 and the second drive unit 3120 in the basic example of the 13th embodiment, so a detailed explanation of the specific configurations will be omitted.

[0156] When performing a rotational torsion test on a specimen T3 using the torsion testing apparatus 3300 of this modified example, for example, the input shaft I is driven at a predetermined rotational speed by the first drive unit 3310, and at the same time, the second drive unit 320 and the third drive unit 3330 are driven to apply torque to the left output shaft OL and the right output shaft OR, respectively.

[0157] By controlling the first drive unit 3310, the second drive unit 3320, and the third drive unit 3330 as described above, a fluctuating torque is applied to each axis of the test specimen T3 while rotating each axis of the test specimen T3, thereby enabling testing under conditions close to actual usage.

[0158] The differential gear unit, like the transmission unit, is a device in which the input shaft I, the left output shaft OL, and the right output shaft OR are connected via gears. When performing a rotational torsional test on this device, the magnitude of the torque applied to the input shaft I does not match the magnitude of the torque applied to the left output shaft OL and the right output shaft OR. Furthermore, the magnitudes of the torque applied to the left output shaft OL and the right output shaft OR do not necessarily match. Therefore, in order to more accurately understand the behavior of the test specimen T3 during the test, it is desirable to be able to measure the torque of the input shaft I, the left output shaft OL, and the right output shaft OR individually. In this modified example, since torque sensors are provided in all three components of the first drive unit 3310, the second drive unit 3320, and the third drive unit 3330, the torque applied to the input shaft I, the left output shaft OL, and the right output shaft OR of the differential gear unit (test specimen T3) can be measured individually.

[0159] Furthermore, the second drive unit 3320 and the third drive unit 3330 may be configured to control the rotational speed of the input shaft I and the rotational speeds of the left output shaft OL and the right output shaft OR to trace the same waveform, or the second drive unit 3320 and the third drive unit 3330 may be configured to control the two to trace different waveforms (for example, such that the speed difference with the input shaft I is in opposite phase).

[0160] Alternatively, the left output shaft OL and the right output shaft OR may be driven at a constant speed, while the input shaft I is driven so that its speed fluctuates at a constant period. Or, the input shaft I, the left output shaft OL, and the right output shaft OR may all be driven so that their rotational speeds fluctuate.

[0161] (Third modified example of the 13th embodiment) Figure 20 is a plan view of a torsion testing apparatus 3400 according to a third modification of the thirteenth embodiment of the present invention. This modified torsion testing apparatus 3400 is an example of a configuration of a torsion testing apparatus suitable for rotational torsion testing of a test specimen T4 having four rotating shafts. Hereinafter, as an example, the case in which a 4WD system is tested as test specimen T4 will be described. Test specimen T4 is an FF-based electronically controlled 4WD system equipped with a transmission, front differential gear, transfer case and electronically controlled multi-plate clutch, which are not shown. Test specimen T4 has an input shaft I connected to the engine, a left output shaft OL and a right output shaft OR connected to the drive shafts for the left and right front wheels, and a rear output shaft OP connected to the propeller shaft that transmits power to the rear wheels. The driving force input to test specimen T4 from the input shaft I is reduced by the transmission provided in test specimen T4 and then distributed to the left output shaft OL and the right output shaft OR via the front differential gear. Furthermore, a portion of the driving force transmitted to the front differential gear is branched off by the transfer case and output from the rear output shaft OP.

[0162] The torsion testing apparatus 3400 of this modified example includes a first drive unit 3410 that drives the input shaft I of the test specimen T4, a second drive unit 3420 that drives the left output shaft OL, a third drive unit 3430 that drives the right output shaft OR, and a fourth drive unit 3440 that drives the rear output shaft OP. The torsion testing apparatus 3400 also includes a control unit C3c that comprehensively controls its operation. The structures of the first drive unit 3410, the second drive unit 3420, the third drive unit 3430, and the fourth drive unit 3440 are all the same as those of the first drive unit 3110 and the second drive unit 3120 of the basic example of the 13th embodiment, so a detailed explanation of the specific configurations will be omitted.

[0163] (14th Embodiment) In the first to thirteenth embodiments described above, the two-axis output servo motor 150A according to the present invention is used in conjunction with a servo motor 150B having one output shaft. However, as in the fourteenth embodiment of the present invention described below, the two-axis output servo motor 150B can also be used on its own.

[0164] Figure 31 is a side view of a torsion testing apparatus 4000 according to the 14th embodiment of the present invention. The torsion testing apparatus 4000 is a device that enables simultaneous rotational torsion testing of two test specimens T3a and T3b using only one 2-axis output servo motor 150A. The torsion testing apparatus 4000 comprises a fixed base 4100, a drive unit 4200, a first reaction unit 4400A, a second reaction unit 4400B, and a control unit C4.

[0165] Figure 32 is an enlarged view of the drive unit 4200. The drive unit 4200 comprises a two-axis output servo motor 150A and a pair of drive transmission units 4200A and 4200B. The two-axis output servo motor 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 reduce the rotation of the first output shaft 150A2a and the second output shaft 150A2b of the two-axis output servo motor 150A, respectively, and transmit it to the input shafts of the test specimens T3a and T3b. Since the drive transmission units 4200A and 4200B have the same configuration, the details of the configuration will only be described for one of the drive transmission units 4200A.

[0166] The drive transmission unit 4200A comprises 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) frame mounted on a fixed base 4100, and comprises a bottom plate 4212 which is a flat plate horizontally positioned on the fixed base 4100, a vertical plate 4214 which is a flat plate standing upright from one end of the upper surface of the bottom plate 4212, and a pair of rib plates 4216 which are connected perpendicularly to the bottom plate 4212 and the vertical plate 4214. The bottom plate 4212, the vertical plate 4214, and the rib plates 4216 are connected to each other by welding. The vertical plate 4214 is positioned perpendicular to the first output shaft 150A2a of the two-axis output servo motor 150A, and has an opening 4214a formed coaxially with the first output shaft 150A2a. A gearbox 4220 is inserted and fixed into the opening 4214a of the vertical plate 4214.

[0167] The first bracket 150A3 of the two-axis output servo motor 150A is bolted to the input-side flange plate 4224 of the reduction gear 4220. The first bracket 150A3 is fixed to the input-side flange plate 4224 via the reinforcing plate 4212, not only by its mounting surface (right side in Figure 31) but also by tapped holes 150A3t provided on its underside. As a result, the input-side flange plate 4224 of the reduction gear 4220 and the first bracket 150A3 of the two-axis output servo motor 150A are connected with high rigidity, enabling high-precision testing.

[0168] The first output shaft 150A2a of the two-axis output servo motor 150A is connected to the input shaft (not shown) of the reduction gear 4220. A chuck device 4260 is attached to the tip of the output shaft 4228 of the reduction gear 4220. The input shaft of the test specimen T3a is attached to the chuck device 4260. The rotation of the first output shaft 150A2a of the two-axis output servo motor 150A is reduced by the reduction gear 4220, the torque is amplified, and then transmitted to the input shaft of the test specimen T3a via the chuck device 4260.

[0169] The gear reducer 4220 is equipped with an oil supply cup 4222, and the internal space of the gear reducer 4220 is filled with lubricating oil, so that each gear constituting the gear reducer 4220 is always completely immersed in the lubricating oil. In torsional tests, a reciprocating torsional load in the normal operating range is applied to the specimen, so the angle of twisting of the specimen is at most a few tens of degrees, and even on the input shaft of the gear reducer, the amplitude of the reciprocating rotation is often less than one rotation (360°). By filling the internal space of the gear reducer 4220 with lubricating oil, oil film breakdown of the gear mechanism constituting the gear reducer is prevented even in this type of use, and the heat dissipation effect of the lubricating oil is enhanced, effectively preventing tooth surface seizure.

[0170] A pulley 4230 is provided on the outer circumference of the output shaft 4228. A rotary encoder 4250 is positioned below the reduction gear 4220 on the vertical plate 4214 of the frame 4210. A timing belt 4240 is wrapped 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. The rotation of the output shaft 4228 of the reduction gear 4220 is transmitted to and detected by the rotary encoder 4250 via the timing belt 4240. The rotary encoder 4250 is connected to a control unit C4, and a signal indicating the rotation detected by the rotary encoder 4250 is sent to the control unit C4.

[0171] Next, the first reaction section 4400A will be described. Note that the second reaction section 4400B has the same configuration as the first reaction section 4400A, so a detailed explanation will be omitted.

[0172] The first reaction unit 4400A comprises a frame 4410, a torque sensor 4420, a spindle 4440, a bearing unit 4460, and a chuck device 4480. The frame 4410 is an angle (L-shaped) frame attached to a fixed base 4100 with bolts B, and comprises a base plate 4412 horizontally positioned on the fixed base 4100, a vertical plate 2414 which is a flat plate that rises upright from one end of the upper surface of the base plate 4412 (the left end in Figure 31), and a pair of rib plates 2416 that are connected perpendicularly to the base plate 4412 and the vertical plate 2414. The base plate 4412, the vertical plate 4214, and the rib plates 4216 are connected to each other by welding. The bearing unit 4460 is fixed to the base plate 4412 with bolts B on the side of the drive unit 4200 that is closer to the vertical plate 2414 and the rib plates 2416.

[0173] The fixed base 4100 is equipped with a first reaction force movement mechanism (not shown) that smoothly moves the first reaction force part 4400A in the direction of the first output shaft 150A2a of the two-axis output servo motor 150A. By loosening the bolt B that fixes the base 4100 to the bottom plate 4412 and activating the first reaction force movement mechanism, the first reaction force part 4400A can be smoothly moved in the direction of the first output shaft 150A2a. The fixed base 4100 is also equipped with a second reaction force movement mechanism (not shown) that smoothly moves the second reaction force part 4400B in the direction of the second output shaft 150A2b of the two-axis output servo motor 150A.

[0174] The torque sensor 4420, spindle 4440, bearing section 4460, and chuck device 4480 are each arranged coaxially with the first output shaft 150A2a of the two-axis output servo motor 150A. One end of the torque sensor 4420 (the left end in Figure 31) is fixed to the vertical plate 4214 of the frame 4410. The other end of the torque sensor 4420 is fixed to one end of the spindle 4440 (the left end in Figure 31), and the chuck device 4480 is attached to the other end of the spindle 4440. The output shaft of the test specimen T3a is attached to the chuck device 4480.

[0175] The torque of the output shaft of test specimen T3a is transmitted to and detected by a torque sensor 4420 via a chuck device 4480 and spindle 4440. The torque sensor 4420 is connected to a control unit C4, and the signal indicating the torque of the output shaft of test specimen T3a detected by the torque sensor 4420 is sent to the control unit C4 for processing.

[0176] Furthermore, the spindle 4440 is rotatably supported by the bearing portion 4460 near the other end (the end on the chuck device 4480 side). Therefore, since the torque sensor 4420 and the spindle 4440 are supported from both sides by the vertical plate 2414 and the bearing portion 4460, it is prevented that the detection error of the torque sensor 4420 will increase due to a large bending moment being applied to the torque sensor 4420.

[0177] When performing a rotational torsion test using the torsion testing apparatus 4000 configured as described above, the input shaft of the test specimen T3a is attached to the chuck device 4260 of the drive transmission unit 4200A, and the output shaft of the test specimen T3a is attached to the chuck device 4480 of the first reaction force unit 4400A. Similarly, the input shaft of the test specimen T3b is attached to the chuck device 4260 of the drive transmission unit 4200B, and the output shaft of the test specimen T3b is attached to the chuck device 4480 of the second reaction force unit 4400B. When the two-axis output servo motor 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 unit 4200A and the drive transmission unit 4200B also rotate in the same phase. This ensures that the same amount of torsion is applied to specimens T3a and T3b, meaning that torsion tests are performed under identical conditions for specimens T3a and T3b.

[0178] According to the configuration of the 14th embodiment described above, torsional tests (fatigue tests) of two test specimens T3a and T3b can be performed simultaneously using one servo motor and control unit C4, making it possible to perform tests efficiently.

[0179] Furthermore, by replacing the drive transmission units 4200A and 4200B with a linear motion converter such as a lead screw mechanism, a tensile / compression testing device can be obtained that repeatedly applies compressive and tensile forces to two test specimens T3a and T3b (or applies compressive force to one of the test specimens T3a and T3b and tensile force to the other). This configuration makes it possible to perform repeated expansion and contraction tests (or tensile tests on test specimen T3a and compression tests on test specimen T3b) on the two test specimens T3a and T3b simultaneously. In addition, by eliminating the first reaction force unit 4400A and the second reaction force unit 4400B, it becomes possible to perform vibration tests on the two test specimens T3a and T3b simultaneously.

[0180] (15th Embodiment) The two-axis output servo motor 150A and servo motor unit 150 according to the embodiment of the present invention can also be used as a drive source for a linear actuator in combination with a linear motion converter such as a lead screw mechanism. Using such a linear actuator, for example, a vibration testing device or a tensile / compression testing device can be realized.

[0181] Figure 33 is a top view of a vibration testing apparatus (vibration device) 5000 according to the 15th embodiment of the present invention. In this embodiment, the vibration testing apparatus 5000 fixes the workpiece to be tested on a table 5100 and uses first, second, and third actuators 5200, 5300, and 5400 to vibrate the table 5100 and the workpiece on it in three orthogonal axis directions. In the following description, the direction in which the first actuator 5200 vibrates the table 5100 (up and down direction in Figure 33) is defined as the X-axis direction, the direction in which the second actuator 5300 vibrates the table 5100 (left and right direction in Figure 33) is defined as the Y-axis direction, and the direction in which the third actuator 5400 vibrates the table, i.e., the vertical direction (direction perpendicular to the plane of the paper in Figure 33), is defined as the Z-axis direction.

[0182] Figure 38 is a block diagram of the control system of a vibration testing apparatus according to an embodiment of the present invention. The first, second, and third actuators 5200, 5300, and 5400 are each provided with vibration sensors 5220, 5320, and 5420, respectively. Based on the outputs of these vibration sensors, the control unit C5 provides feedback control to the first, second, and third actuators 5200, 5300, and 5400 (specifically, the servo motor units 150X, 150Y, and 150Z), thereby exciting the table 5100 and the workpiece mounted thereon at a desired amplitude and frequency (these parameters are usually set as a function of time). The servo motor units 150X, 150Y, and 150Z are identical to the servo motor unit 150 in the first embodiment.

[0183] The first, second, and third actuators 5200, 5300, and 5400 are configured with motors, power transmission members, etc., mounted on base plates 5202, 5302, and 5402, respectively. These base plates 5202, 5302, and 5402 are fixed to the device base 5002 by bolts (not shown).

[0184] Furthermore, adjusters A are positioned on the device base 5002 at multiple locations close to the base plates 5202, 5302, and 5402. Each adjuster A has a female threaded portion A1 fixed to the device base 5002 with bolts AB, and a male threaded portion A2 screwed into the female threaded portion A1. The male threaded portion A2 is a cylindrical member with screw threads formed on its cylindrical surface. By engaging the male threaded portion A2 with a screw hole formed in the female threaded portion A1 and rotating it, the male threaded portion A2 can be advanced and retracted relative to the corresponding base plate. One end of the male threaded portion A2 (the side proximal to the corresponding base plate) is formed in a substantially spherical shape, and by bringing this protrusion into contact with the side surface of the corresponding base plate, the position of the base plate can be finely adjusted. Additionally, a hexagonal hole for a hex wrench (not shown) is formed at the other end of the male threaded portion A2 (the side distal to the corresponding base plate). Furthermore, after the base plates 5202, 5302, and 5402 are fixed in place, a nut A3 is attached to the male thread portion A2 to prevent it from loosening due to vibrations transmitted from the base plate to the adjuster A during vibration testing. The nut A3 is attached so that one end face abuts against the female thread portion A1. From this state, the nut A3 is screwed in to push in the female thread portion A1, applying axial force to the male thread portion A2 and the female thread portion A1. This axial force generates frictional force on the threads of the male thread portion A2 and the female thread portion A1, preventing the female thread portion A1 from loosening from the male thread portion A2.

[0185] Next, the configuration of the first actuator 5200 will be described. Figure 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 Figure 33). Part of this side view is cut out to show the internal structure. Figure 35 is a top view of the first actuator 5200, partially cut out to show the internal structure. In the following description, the direction along the X-axis from the first actuator 5200 toward the table 5100 is defined as the "positive X-axis direction," and the direction along the X-axis from the table 5100 toward the first actuator is defined as the "negative X-axis direction."

[0186] As shown in Figure 34, a frame 5222, consisting of multiple beams 5222a welded to each other and a top plate 5222b, is fixed to the base plate 5202 by welding. In addition, the bottom plate 5242 of the support mechanism 5240, which supports the drive mechanism 5210 for vibrating the table 5100 (Figure 33) and the connecting mechanism 5230 for transmitting the vibration motion from the drive mechanism 5210 to the table 5100, is fixed to the top plate 5222b of the frame 5222 via bolts (not shown).

[0187] The drive mechanism 5210 includes a servo motor unit 150X, a coupling 5260, a bearing section 5216, a ball screw 5218, and a ball nut 5219. The coupling 5260 connects the drive shaft 152X of the servo motor unit 150X to the ball screw 5218. The bearing section 5216 is supported by a bearing support plate 5244, which is welded perpendicularly to the bottom plate 5242 of the support mechanism 5240, and rotatably supports the ball screw 5218. The ball nut 5219 engages with the ball screw 5218 while being supported by the bearing support plate 5244 so as not to move around its axis. Therefore, when the servo motor unit 150X is driven, the ball screw rotates, and the ball nut 5219 moves back and forth in its axial direction (i.e., 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. The table 5100 can then be excited in the X-axis direction with a desired amplitude and period by controlling the servo motor unit 150X to switch its rotation direction at short intervals.

[0188] A motor support plate 5246 is welded perpendicularly to the upper surface of the bottom plate 5242 of the support mechanism 5240. A servo motor unit 150X is cantilevered on one side of the motor support plate 5246 (the side in the negative X-axis direction) such that the drive shaft 152X is perpendicular to the motor support plate 5246. The motor support plate 5246 is provided with an opening 5246a, through which the drive shaft 152X of the servo motor unit 150X passes and is connected to a ball screw 5218 on the other side of the motor support plate 5246.

[0189] Furthermore, since the servo motor unit 150X is cantilevered to the motor support plate 5246, the motor support plate 5246 is subjected to significant bending stress, particularly at the welded joint with the base plate 5242. To alleviate this bending stress, a rib 5248 is provided between the base plate 5242 and the motor support plate 5246.

[0190] The bearing section 5216 has a pair of angular contact ball bearings 5216a and 5216b (5216a is on the negative X-axis side, and 5216b is on the positive X-axis side) that are assembled face-to-face. The angular contact ball bearings 5216a and 5216b are housed in the hollow portion of the bearing support plate 5244. A bearing pressing plate 5216c is provided on one side of the angular contact ball bearing 5216b (the side on the positive X-axis side), and by fixing this bearing pressing plate 5216c to the bearing support plate 5244 using bolts 5216d, the angular contact ball bearing 5216b is pushed in the negative X-axis direction. In addition, in the ball screw 5218, a threaded portion 5218a is formed on the cylindrical surface adjacent to the bearing section 5216 on the negative X-axis side. A collar 5217 with an internal thread formed on its inner circumference is attached to this threaded portion 5218. By rotating the collar 5217 relative to the ball screw 5218 and moving it in the positive X-axis direction, the angular contact ball bearing 5216a is pushed in the positive X-axis direction. In this way, the angular contact ball bearings 5216a and 5216b are pushed toward each other, so that they are in close contact with each other and an appropriate preload is applied to the bearings 5216a and 5216b.

[0191] Next, the configuration of the connecting section 5230 will be described. The connecting section 5230 includes 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.

[0192] The nut guide 5232 is fixed to the ball nut 5219. The pair of Y-axis rails 5234 are both rails extending in the Y-axis direction and are fixed side by side vertically to the X-positive end of the nut guide 5232. The pair of Z-axis rails 5235 are both rails extending in the Z-axis direction and are fixed side by side in the Y-axis direction to the X-negative end of the table 5100. The intermediate stage 5231 is a block in which a Y-axis runner block 5231a that engages with each of the Y-axis rails 5234 is provided on the X-negative side, and a Z-axis runner block 5231b that engages with each of the Z-axis rails 5235 is provided on the X-positive side, and is configured to be slidable relative to both the Y-axis rails 5234 and the Z-axis rails 5235.

[0193] In other words, the intermediate stage 5231 is slidable in the Z-axis direction relative to the table 5100 and slidable in the Y-axis direction relative to the nut guide 5232. Therefore, the nut guide 5231 is slidable in both the Y-axis and Z-axis directions relative to the table 5100. As a result, even if the table 5100 is vibrated in the Y-axis and / or Z-axis directions by other actuators 5300 and / or 5400, the nut guide 5232 will not be displaced as a result. In other words, bending stress caused by the displacement of the table 5100 in the Y-axis and / or Z-axis directions will not be applied to the ball screw 5218, bearing 5216, coupling 5260, etc.

[0194] A pair of X-axis rails 5237 are rails that 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 blocks 5233 engage with each of the X-axis rails 5237 and are 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 blocks 5233 are fixed to the bottom of the runner block mounting member 5238. In this way, the nut guide 5232 is guided to the X-axis rails 5237 via the runner block mounting member 5238 and the X-axis runner blocks 5233, thereby allowing movement only in the X-axis direction.

[0195] Thus, 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 table 5100 that engages with the nut guide 5232 move back and forth in the X-axis direction.

[0196] A position detection means 5250 is positioned on one side of the runner block mounting member 5238 on the Y-axis side (the front side in Figure 34, and the right side in Figure 35) 5238a. 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 5238a of the runner block mounting member 5238, and a sensor support plate 5253 that supports the proximity sensors 5251. Each proximity sensor 5251 is an element capable of detecting whether an object is in close proximity (for example, within 1 millimeter) to it. Since the side 5238a of the runner block mounting member 5238 and the proximity sensors 5251 are sufficiently far apart, the proximity sensors 5251 can detect whether there is a detection plate 5252 in front of each proximity sensor 5251. The control unit C5 of the vibration testing apparatus 5000 can, for example, use the detection results of the proximity sensor 5251 to provide feedback control to the servo motor unit 150X (Figure 38).

[0197] Furthermore, a restricting block 5236 is provided on the bottom plate 5242 of the support mechanism 5240, positioned to sandwich the X-axis runner block 5233 from both sides in the X-axis direction. This restricting block 5236 is intended to limit the range of movement of the nut guide 5232. That is, if the servo motor unit 150X is driven to continuously move the nut guide 5232 in the positive X-axis direction, eventually the restricting block 5236 positioned on the positive X-axis side and the runner block mounting member 5238 will come into contact, preventing the nut guide 5232 from moving any further in the positive X-axis direction. The same applies when continuously moving the nut guide 5232 in the negative X-axis direction; the restricting block 5236 positioned on the negative X-axis side and the runner block mounting member 5238 will come into contact, preventing the nut guide 5232 from moving any further in the negative X-axis direction.

[0198] 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 and Y axes are swapped). Therefore, a detailed explanation of the second actuator 5300 will be omitted.

[0199] Next, the configuration of the third actuator 5400 according to an embodiment of the present invention will be described. Figure 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 Figure 16). This side view is also partially cut out to show the internal structure. Figure 37 is a side view of the table 5100 and the third actuator 5400 according to an embodiment of the present invention viewed from the Y-axis direction (from the left to the right in Figure 33). Figure 37 is also partially cut out to show the internal structure. In the following description, the direction along the Y-axis from the second actuator 5300 toward the table 5100 is defined as the positive Y-axis direction, and the direction along the Y-axis from the table 5100 toward the second actuator 5300 is defined as the negative Y-axis direction.

[0200] As shown in Figures 36 and 37, a frame 5422 is provided on the base plate 5402, consisting of a plurality of vertically extending beams 5422a and a top plate 5422b positioned to cover these beams 5422a from above. The lower end of each beam 5422a is welded to the upper surface of the base plate 5402, and the upper end is welded to the lower surface of the top plate 5422b. In addition, a bearing support plate 5442 of the support mechanism 5440 is fixed to the top plate 5422b of the frame 5422 via bolts (not shown). This bearing support plate 5442 is a member for supporting the drive mechanism 5410 for vibrating the table 5100 (Figure 33) in the vertical direction, and the connecting mechanism 5430 for transmitting the vibration motion from the drive mechanism 5410 to the table.

[0201] The drive mechanism 5410 includes a servo motor unit 150Z, a coupling 5460, a bearing section 5416, a ball screw 5418, and a ball nut 5419. The coupling 5460 connects the drive shaft 152Z of the servo motor unit 150Z to the ball screw 5418. The bearing section 5416 is fixed to the aforementioned bearing support plate 5442 and rotatably supports the ball screw 5418. The ball nut 5419 engages with the ball screw 5418 while being supported by the bearing support plate 5442 so as not to move around its axis. Therefore, when the servo motor unit 150Z is driven, the ball screw rotates, and the ball nut 5419 moves back and forth in its axial direction (i.e., the Z-axis direction). This movement 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. Furthermore, by controlling the servo motor unit 150Z to switch its rotation direction at short intervals, the table 5100 can be excited in the Z-axis direction (vertical direction) with a desired amplitude and period.

[0202] A motor support plate 5446 extending horizontally (in the XY plane) is fixed to the lower surface of the bearing support plate 5442 of the support mechanism 5440 via two connecting plates 5443. 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, through which the drive shaft 152Z of the servo motor unit 150Z passes and is connected to a ball screw 5418 on the upper side of the motor support plate 5446.

[0203] In this embodiment, since the axial dimensions (vertical and Z-axis directions) of the servo motor unit 150Z are greater than the height of the frame 5422, most of the servo motor unit 150Z is positioned lower than the base plate 5402. For this reason, the device base 5002 is provided with a cavity 5002a for housing the servo motor unit 150Z. The base plate 5402 is also provided with an opening 5402a for passing the servo motor unit 150Z through.

[0204] The bearing portion 5416 is provided so as to penetrate the bearing support plate 5442. Note that the structure of the bearing portion 5416 is the same as that of the bearing portion 5216 in the first actuator 5200 (Figures 34 and 35), so a detailed explanation is omitted.

[0205] Next, the configuration of the connecting section 5430 will be described. The connecting section 5430 includes 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.

[0206] The movable frame 5432 has a frame portion 5432a fixed to a 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. The pair of Y-axis rails 5435 are both rails extending in the Y-axis direction and are fixed side by side in the X-axis direction to the upper surface of the top plate 5432b of the movable frame 5432. The pair of X-axis rails 5434 are both rails extending in the X-axis direction and are fixed side by side in the Y-axis direction to the lower surface of the table 5100. The intermediate stage 5431 is a block with an X-axis runner block 5431a at the top that engages with the X-axis rail 5434 and a Y-axis runner block 5431b at the bottom that engages with each of the Y-axis rails 5435, and is configured to slide relative to both the X-axis rail 5434 and the Y-axis rail 435. Furthermore, one intermediate stage 5431 is provided at each point where the X-axis rail 5434 and the Y-axis rail 5435 intersect. Since there are two X-axis rails 5434 and two Y-axis rails 5435, they intersect at four points. Therefore, in this embodiment, four intermediate stages 5431 are used.

[0207] Thus, each of the intermediate stages 5431 is slidable in the X-axis direction relative to the table 5100 and slidable in the Y-axis direction relative to the movable frame 5432. In other words, the movable frame 5432 is slidable in both the X-axis and Y-axis directions relative to the table 5100. Therefore, even if the table 5100 is vibrated in the X-axis direction and / or Y-axis direction by other actuators 5200 and / or 5300, the movable frame 5432 will not be displaced as a result. In other words, bending stress caused by the displacement of the table 5100 in the X-axis direction and / or Y-axis direction will not be applied to the ball screw 5418, bearing 5416, coupling 5460, etc.

[0208] Furthermore, in this embodiment, the movable frame 5432 has a wider spacing between the X-axis rail 5434 and the Y-axis rail 5435 compared to the Y-axis rail 5234 and Z-axis rail 5235 of the first actuator 5200, in order to support the relatively heavy table 5100 and workpiece. Therefore, if the table 5100 and the movable frame 5432 were connected by only one intermediate stage, as in the first actuator 5200, the intermediate stage would become larger, increasing the load on the movable frame 5432. For this reason, in this embodiment, a small intermediate stage 5431 is placed at each point where the X-axis rail 5434 and the Y-axis rail 5435 intersect, thereby minimizing the load on the movable frame 5432.

[0209] The two pairs of Z-axis rails 5437 are rails that extend in the Z-axis direction and are fixed in pairs to each of the side walls 5432c of the movable frame 5432, aligned in the Y-axis direction. The Z-axis runner blocks 5433 engage with each of these Z-axis rails 5437 and are slidable along the Z-axis rails 5437. The Z-axis runner blocks 5433 are fixed to the upper surface of the top plate 5422b of the frame 5422 via runner block mounting members 5438. The runner block mounting member 5438 has a side plate 5438a that is positioned approximately parallel to the side wall 5432c of the movable frame 5432, and a bottom plate 5438b that is fixed to the lower end of the side plate 5438a, and has an overall L-shaped cross-section. Furthermore, in this embodiment, when a workpiece with a high center of gravity and heavy weight is fixed on the table 5100, large moments around the X-axis and / or Y-axis are easily 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 plates 5438a and bottom plate 5438b at both ends of the runner block mounting member 5438 in the Y-axis direction, and a second rib 5438d is provided between this pair of first ribs 5438c.

[0210] Thus, the Z-axis runner block 5433 is fixed to the frame 5422 and is slidable relative to the Z-axis rail 5437. Therefore, the movable frame 5432 is slidable in the vertical direction, and movement of the movable frame 5432 in directions other than vertical is restricted. Because the movement direction of the movable frame 5432 is restricted to the vertical direction only, when the servo motor unit 150Z is driven to rotate the ball screw 5418, the movable frame 5432 and the table 5100 that engages with the movable frame 5432 move back and forth in the vertical direction.

[0211] Furthermore, the third actuator 5400 is also provided with a position detection means (not shown) similar to the position detection means 5250 of the first actuator 5200 (Figures 34 and 35). Based on the detection results of this position detection means, the control unit C5 of the vibration testing device 5000 can control the height of the movable frame 5432 so that it is within a predetermined range (Figure 38).

[0212] As described above, in this embodiment, two pairs of rails and an intermediate stage configured to slide relative to these rails are provided between each actuator and the table 5100, whose drive axes are orthogonal to each other. This allows the table 5100 to slide in any direction on a plane perpendicular to the drive direction of each actuator. Therefore, even if the table 5100 is displaced by one actuator, no load or moment resulting from this displacement is applied to the other actuators, and the engagement between the other actuators and the table 5100 via the intermediate stage is maintained. In other words, even if the table is displaced to any position, each actuator remains capable of displacing the table. For this reason, in this embodiment, the three actuators 5200, 5300, and 5400 can be driven simultaneously to excite the table 5100 and the workpiece fixed thereon in three axial directions.

[0213] In this embodiment, as described above, a connecting section is provided between the actuators 5200, 5300, and 5400 and the table 5100, which is equipped with a guide mechanism combining rails and runner blocks. A similar guide mechanism is also provided for the actuators 5200, 5300, and 5400, and this guide mechanism is used to guide the nuts of the ball screw mechanisms of each actuator.

[0214] Furthermore, while ultra-low inertia servo motors are used as torque generators in each of the above embodiments, the present invention is not limited to these. Configurations using other types of electric motors (e.g., inverter motors) with a small rotor moment of inertia and capable of driving at high acceleration or high jerk are also included in the present invention. In this case, as in each of the above embodiments, an encoder may be provided on the electric motor, and a configuration may be adopted in which feedback control is performed based on the rotational state of the output shaft of the electric motor detected by the encoder (e.g., rotational speed or angular position).

[0215] Furthermore, although the above embodiments are examples of applying the present invention to a durability testing apparatus for power transmission systems in automobiles, the present invention is not limited to this and can be used for various applications in industry in general. For example, the present invention can be used to evaluate the mechanical properties and durability of motorcycles, agricultural machinery, construction machinery, railway vehicles, ships, aircraft, power generation systems, water supply and drainage systems, or various components that constitute them.

[0216] The above describes the embodiment, but 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, a servo motor unit 150 (or torque-applying servo motor unit 132) is used, which consists of one servo motor 150B (having one output shaft) and one two-axis output servo motor 150A connected in two stages. However, a configuration using a servo motor unit in which one servo motor 150B and multiple two-axis output servo motors 150A are connected in three or more stages is also possible.

[0217] <Addendum> To further expand the application range of servo motor-type testing equipment, there is a need for even higher output power while maintaining the high acceleration characteristics of ultra-low inertia servo motors.

[0218] Furthermore, because the cost of the servo motor accounts for a large proportion of the manufacturing cost of servo motor-type testing equipment, there is a demand for servo motor-type testing equipment that can test multiple test specimens simultaneously using a single servo motor.

[0219] However, simply increasing the output of a servo motor necessitates strengthening each part of the servo motor, resulting in a larger size and increased weight that outweighs the increase in output. Furthermore, this increases the servo motor's moment of inertia-to-output ratio (the ratio of the moment of inertia to the servo motor's output), leading to a decrease in acceleration characteristics (including jerk) and a reduction in the frequency range of variable loads that can be output.

[0220] Furthermore, conventional servo motors have only one output shaft, so in order to test multiple test specimens simultaneously, it is necessary to install a gear mechanism or similar to distribute power, which leads to problems such as increased frictional resistance and the need for larger testing equipment.

[0221] According to one embodiment of the present invention, a two-axis output servo motor is provided, comprising a cylindrical main frame, a substantially flat first bracket attached to one axial end of the main frame, a substantially flat second bracket attached to the other axial end of the main frame, and a drive shaft that passes through the hollow portion of the main frame, penetrates the first bracket and the second bracket, and is rotatably supported by bearings provided on the first bracket and the second bracket, wherein one end of the drive shaft protrudes outward from the first bracket to serve as a first output shaft that outputs driving force to the outside, and the other end protrudes outward from the second bracket to serve as a second output shaft.

[0222] The first bracket and the second bracket may be configured to have a first mounting surface formed on the opposite side of their mutually opposing surfaces, with tapped holes for mounting a two-axis output servo motor.

[0223] The first bracket and the second bracket may also be configured to have a second mounting surface perpendicular to the first mounting surface, with tapped holes for attaching a two-axis output servo motor.

[0224] A rotary encoder for detecting the rotational position of the drive shaft may be provided on at least one of the first bracket and the second bracket.

[0225] According to one embodiment of the present invention, a servo motor unit is provided comprising: a cylindrical main frame; a load-side bracket attached to one axial end of the main frame; a non-load-side bracket attached to the other axial end of the main frame; a drive shaft passing through the hollow portion of the main frame, penetrating the first bracket and the second bracket, and rotatably supported by bearings provided on the load-side bracket and the non-load-side bracket, respectively, wherein only one end of the drive shaft protrudes outward from the load-side bracket, constituting an output shaft that outputs driving force to the outside; the above-mentioned two-axis output servo motor; a connecting member connecting the load-side bracket and the second bracket at a predetermined distance; a coupling connecting the output shaft of the second servo motor and the second output shaft of the two-axis output servo motor; and a drive control unit that drives the second servo motor and the two-axis output servo motor in the same phase.

[0226] The servo motor unit described above includes the two-axis output servo motor, and a rotary encoder for detecting the rotational position of the drive shaft is attached to either the load-side bracket or the non-load-side bracket. The drive control unit may be configured to control the drive of the second servo motor and the two-axis output servo motor based on the signal output by the rotary encoder.

[0227] The servo motor unit described above includes the two-axis output servo motor, and the drive control unit may be configured to control the drive of the second servo motor and the two-axis output servo motor based on the signal output by one of the rotary encoders.

[0228] According to one embodiment of the present invention, a rotational torsion test device is provided, comprising: a first drive shaft to which one end of a workpiece is attached and which rotates about a predetermined rotation axis; a second drive shaft to which the other end of the workpiece is attached and which rotates about the rotation axis; a load application unit that supports the first drive shaft and rotates the first drive shaft to apply a torsional load to the workpiece; at least one first bearing that rotatably supports the load application unit about the rotation axis; a rotational drive unit that rotates the first drive shaft and the load application unit in the same phase; and a torque sensor that detects the torsional load. The rotational drive unit rotates the workpiece via the first drive shaft and the second drive shaft, and the load application unit applies a load to the workpiece by giving a phase difference to the rotation of the first drive shaft and the second drive shaft. The load application unit comprises a frame having a cylindrical shaft portion into which the first drive shaft is inserted, the frame being supported by a first bearing at the shaft portion and supporting the first drive shaft, and the torque sensor being attached to the portion inserted into the shaft portion of the first drive shaft and configured to detect the torsional load of that portion. The load application unit comprises the servo motor unit described above.

[0229] The rotary torsion testing apparatus comprises a drive power supply unit located outside the load application unit that supplies drive power to a servo motor unit, a drive power transmission path that transmits drive power from the drive power supply unit to the servo motor unit, a torque signal processing unit located outside the load application unit that processes torque signals output by a torque sensor, and a torque signal transmission path that transmits torque signals from the torque sensor to the torque signal processing unit, wherein the drive power transmission path comprises an external drive power transmission path located outside the load application unit, an internal drive power transmission path located inside the load application unit that rotates together with the load application unit, and a first slip ring section that connects the external drive power transmission path and the internal drive power transmission path, and the torque signal transmission path comprises an external torque signal transmission path located outside the load application unit, an internal torque signal transmission path wired inside the load application unit that rotates together with the load application unit, and a second slip ring section that connects the external torque signal transmission path and the internal torque signal transmission path, wherein the second slip ring section may be located separately from the first slip ring section.

[0230] The rotary drive unit may be configured to include a second motor and a drive force transmission unit that transmits the driving force of the second motor to a load application unit and a second drive shaft to rotate them in the same phase, and the drive force transmission unit may be configured to include a first drive force transmission unit that transmits the driving force of the second motor to the second drive shaft and a second drive force transmission unit that transmits the driving force of the second motor to the load application unit.

[0231] The first drive force transmission unit and the second drive force transmission unit may each be equipped with an endless belt mechanism, and the first drive force transmission unit may be configured to include a third drive shaft driven by a second motor and arranged parallel to the rotation shaft, a first drive pulley fixed coaxially to the third drive shaft, a first driven pulley fixed coaxially to the load application unit, and a first endless belt stretched between the first drive pulley and the first driven pulley, and the second drive force transmission unit may be configured to include a fourth drive shaft coaxially connected to the third drive shaft, a second drive pulley fixed to the fourth drive shaft, a second driven pulley fixed to the first drive shaft, and a second endless belt stretched between the second drive pulley and the second driven pulley.

[0232] According to one embodiment of the present invention, a torsion testing device is provided that applies torque to the input and output shafts of a test specimen, which is a power transmission device, comprising a first drive unit connected to the input shaft of the test specimen and a second drive unit connected to the output shaft of the test specimen, wherein the first drive unit and the second drive unit each comprise a servo motor unit, a reduction gear for reducing the rotation of the drive shaft of the servo motor unit, a chuck to which the input or output shaft of the test specimen is attached and which transmits the output of the reduction gear to the input or output shaft of the test specimen, a torque sensor that transmits the output of the reduction gear to the chuck and detects the torque output by the reduction gear, and a tachometer for detecting the rotational speed of the chuck.

[0233] The reduction gear comprises a spindle connecting a torque sensor and a chuck, and a bearing section that rotatably supports the spindle. The reduction gear also comprises a gear case, a bearing, and a gear mechanism supported by the gear case via the bearing. The load on the power transmission shaft, including the gear mechanism of the reduction gear that transmits the driving force of the servo motor to the test specimen, the torque sensor, and the spindle, may be supported by the spindle and the gear mechanism of the reduction gear.

[0234] According to one embodiment of the present invention, a torsion testing apparatus for simultaneously testing a first test specimen and a second test specimen comprises the above-mentioned two-axis output servo motor, a first drive transmission unit that transmits the rotation of the first output shaft to one end of the first test specimen, a first reaction force unit that fixes the other end of the first test specimen, a second drive transmission unit that transmits the rotation of the second output shaft to one end of the second test specimen, and a second reaction force unit that fixes the other end of the second test specimen, wherein the first drive transmission unit and the second drive transmission unit are equipped with a chuck device for attaching one end of the first or second test specimen, the first reaction force unit and the second reaction force unit are equipped with a chuck device for attaching the other end of the first or second test specimen, and the apparatus may also be configured to include a torque sensor for detecting the torque applied to the first or second test specimen.

[0235] The first drive transmission unit and the second drive transmission unit may be configured to 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.

[0236] According to one embodiment of the present invention, a torsion testing apparatus is provided comprising a frame, a servo motor unit fixed to the frame, a servo motor, a reduction mechanism for reducing the rotation of the servo motor, a coupling connecting the input shaft of the reduction mechanism and the drive shaft of the servo motor, a first gripping part fixed to the output shaft of the reduction mechanism for gripping one end of the test specimen, and a second gripping part fixed to the frame for gripping the other end of the test specimen.

[0237] According to one embodiment of the present invention, a linear actuator is provided comprising the above-mentioned servo motor unit, a lead screw, a coupling connecting the lead screw and the drive shaft of the servo motor unit, a nut engaging with the lead screw, a linear guide restricting the direction of movement of the nut to only the axial direction of the lead screw, and a support plate to which the servo motor and the linear guide are fixed.

[0238] According to one embodiment of the present invention, a vibration device is provided comprising a table for mounting a workpiece and a first actuator capable of vibrating the table in a first direction, wherein the first actuator comprises the above-mentioned servo motor unit and a ball screw mechanism that converts the rotational motion of the servo motor unit into translational motion in a first or second direction.

[0239] According to one embodiment of the present invention, a vibration device is provided comprising: a table for mounting a workpiece; a first actuator capable of vibrating the table in a first direction; a second actuator capable of vibrating the table in a second direction perpendicular to the first direction; a first connecting means for slidably connecting the table to the first actuator in a second direction; and a second connecting means for slidably connecting the table to the second actuator in a first direction, wherein the first actuator and the second actuator each comprise a servo motor unit and a ball screw mechanism for converting the rotational motion of the servo motor unit into translational motion in a first or second direction.

[0240] According to one embodiment of the present invention, a vibration device is provided comprising: a table for mounting a workpiece; a first actuator capable of vibrating the table in a first direction; a second actuator capable of vibrating the table in a second direction perpendicular to the first direction; a third actuator capable of vibrating the table in a third direction perpendicular to both the first and second directions; a first connecting means for slidably connecting the table to the first actuator in the second and third directions; a second connecting means for slidably connecting the table to the second actuator in the first and third directions; and a third connecting means for slidably connecting the table to the third actuator in the first and second directions, wherein the first actuator, the second actuator, and the third actuator each comprise the above-mentioned servo motor unit and a ball screw mechanism for converting the rotational motion of the servo motor unit into translational motion in the first, second, or third direction.

[0241] According to one embodiment of the present invention, a torsion testing apparatus is provided, comprising: a first servo motor; a cylindrical casing; a second servo motor fixed inside the casing; and a torque-applying unit having a reduction gear that includes a frame fixed inside the casing, an input shaft to which the output shaft of the servo motor is connected, and an output shaft that reduces the rotation of the input shaft and outputs it, and which protrudes from the casing; a first shaft to which a workpiece is attached and which has one end connected to the output shaft of the reduction gear; a second shaft which has one end connected to the output shaft of the motor; a first gearbox having a connection portion to which the output shaft of the reduction gear and the casing of the torque-applying unit are connected, and which transmits the rotational motion of the output shaft and the casing by gears; and a second gearbox having a connection portion to which the other end of the first shaft and the other end of the second shaft are connected, and which transmits the rotational motion of the first shaft and the second shaft by gears.

[0242] According to the present invention, since power is circulated via the first gearbox and the second gearbox, power loss is reduced compared to conventional configurations in which power is circulated by a belt mechanism, resulting in a torsion testing device with lower running costs.

[0243] According to one embodiment of the present invention, a power simulator is provided, comprising: an output shaft; a control unit that controls the rotation of the output shaft to generate simulated power that simulates a predetermined power; a rotatably supported load-applying unit that applies torque instructed by the control unit to the output shaft; and a rotational drive unit that rotationally drives the load-applying unit at a rotational speed instructed by the control unit, wherein the load-applying unit is equipped with a servo motor whose rotational shaft is connected to the output shaft.

[0244] According to the configuration of the embodiment of the present invention, an electric power simulator is provided that can accurately simulate torque fluctuations of high frequency components even at high rotational speeds.

[0245] By designating both ends of the drive shaft as a first output shaft and a second output shaft, output distribution becomes possible without adding power distribution means such as a gear mechanism, thus preventing an increase in frictional resistance and an increase in the size of the test equipment that would be associated with the addition of power distribution means. Furthermore, with this configuration, it becomes possible to combine the outputs by connecting one of the first and second output shafts to the output shaft of another servo motor, making it possible to achieve high output while suppressing the increase in the size of the servo motor and the resulting decrease in acceleration characteristics due to the increase in moment of inertia.

Claims

1. A frame that is supported to rotate freely, The electric motor is mounted on the aforementioned frame, Equipped with, The aforementioned electric motor is capable of controlling its drive amount and is located within the hollow portion of the frame. The frame is configured to be connectable to an external drive means, The system is configured to output a result obtained by adding the rotation generated by the electric motor to the rotation given to the frame by the external drive means. Load application section.

2. The frame is provided with a bearing portion that rotatably supports the frame, The aforementioned frame, The body to which the aforementioned electric motor is attached, A shaft portion is rotatably supported by the bearing portion, The load-applying unit according to claim 1.

3. The body portion is cylindrical, The electric motor is located within the hollow portion of the body. The load-applying unit according to claim 2.

4. The electric motor is equipped with a motor case, The motor case is fixed to the frame via a plurality of fixing rods. A load-applying unit according to any one of claims 1 to 3.

5. The motor case comprises a bracket on which a second bearing is provided that rotatably supports the shaft of the electric motor. One end of the fixing rod is fixed to the bracket. The load-applying unit according to claim 4.

6. The other end of the aforementioned fixing rod is fixed to the body portion. A load-applying unit according to claim 5, indirectly referencing claim 2.

7. A load-applying unit according to any one of claims 1 to 6, Mechanical testing equipment.

8. A load-applying unit according to any one of claims 1 to 6, A first workpiece mounting section to which one end of the test specimen is attached, A second workpiece mounting section to which the other end of the test specimen is attached, Equipped with, Mechanical testing equipment.

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