Load provision part and machine 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 testing apparatus. [Background technology]

[0002] By adopting an ultra-low inertia servo motor, which has significantly reduced inertia compared to conventional servo motors, the inventors have put into practical use various servo motor-type fatigue testing devices and vibration testing devices that are capable of applying repeated loads at high frequencies of several tens to several hundreds of Hz (for example, Patent Document 1).

[0003] The range of applications of the servo motor type testing equipment described above is expanding rapidly because it solves many of the serious issues that conventional hydraulic testing equipment had (for example, the need to install large-scale hydraulic supply facilities such as oil tanks and hydraulic piping, the need to regularly replace large amounts of hydraulic oil, and work environment and soil contamination due to hydraulic oil leakage). [Prior art documents] [Patent documents]

[0004] [Patent Document 1] International Publication No. 2008 / 133187 Summary of the Invention [Problem to be solved by the invention]

[0005] SUMMARY OF THE PRESENT EMBODIMENT An object of the present invention is to provide a tire testing apparatus capable of testing tires under simulated actual running conditions. [Means for solving the problem]

[0006] According to one embodiment of the present invention, there is provided a tire testing apparatus comprising: a rotating drum having a simulated road surface formed on its outer peripheral surface; a mechanism for rotatably supporting a test specimen tire while mounted on a wheel and pressing the tread portion of the tire against the simulated road surface; a torque imparting unit for imparting torque to the tire; and a rotational drive motor for rotationally driving the rotating drum and a casing of the torque imparting unit.

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

[0008] The tire testing apparatus may further include a power transmission section that transmits the driving force of the motor to the rotating drum and the torque applying unit to rotate 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 for pressing the tread portion of the tire against the simulated road surface may be an alignment control mechanism capable of adjusting the alignment of the tire with respect to the simulated road surface.

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

[0012] In the above tire testing apparatus, the alignment control mechanism may include a slip angle adjustment unit capable of adjusting the slip angle of the tire with respect to the simulated road surface by tilting the rotation axis of the tire about a line perpendicular to the simulated road surface.

[0013] In the tire testing apparatus described above, the alignment control mechanism may include a camber angle adjustment unit capable of adjusting the camber angle by tilting the rotation axis of the tire relative to the rotation axis of the rotary drum.

[0014] The above tire testing apparatus may be configured to include a traverse device that moves the tire in the direction of the rotation axis.

[0015] In the tire testing apparatus described above, the rotation drive motor may be an inverter motor. Effect of the Invention

[0016] The configuration of one embodiment of the present invention allows for testing of tires under simulated real-world driving conditions. [Brief description of the drawings]

[0017] [Figure 1] FIG. 1 is a side view of a two-axis output servomotor according to an embodiment of the present invention. [Diagram 2] FIG. 2 is a side view of the servo motor unit according to the embodiment of the present invention. [Diagram 3] FIG. 11 is a vertical sectional view of a modified example of the servo motor unit according to the embodiment of the present invention. [Figure 4] FIG. 1 is a side view of a rotary torsion testing device according to a first embodiment of the present invention. [Diagram 5] FIG. 2 is a vertical cross-sectional view of the vicinity of a load applying portion of the rotary torsion testing device according to the first embodiment of the present invention. [Figure 6] FIG. 1 is a block diagram showing a schematic configuration of a control system of a rotary torsion testing apparatus according to a first embodiment of the present invention. [Figure 7] FIG. 4 is an external view of a power simulator according to a modified example of the first embodiment of the present invention. [Figure 8] FIG. 4 is an external view of a power simulator according to a modified example of the first embodiment of the present invention. [Figure 9] FIG. 4 is a side view of a testing device including a power simulator according to a modified example of the first embodiment of the present invention. [Figure 10] FIG. 4 is a partially enlarged view of a testing device including a power simulator according to a modified example of the first embodiment of the present invention. [Figure 11] FIG. 5 is a plan view of a rotary torsion testing device according to a second embodiment of the present invention. [Figure 12] FIG. 5 is a side view of a rotary torsion testing device according to a second embodiment of the present invention. [Figure 13] FIG. 11 is a vertical cross-sectional view of a load applying portion and its surroundings of a rotary torsion testing device according to a second embodiment of the present invention. [Figure 14] 11A and 11B are a top view and a side view of a torsion test device according to a third embodiment of the present invention. [Figure 15] FIG. 11 is a side cross-sectional view of a torque applying section of a torsion test device according to a third embodiment of the present invention. [Figure 16] FIG. 11 is a top view of a torsion test device according to a fourth embodiment of the present invention. [Figure 17] FIG. 13 is a top view of a torsion test device according to a fifth embodiment of the present invention. [Figure 18] FIG. 13 is a top view of a torsion test device according to a sixth embodiment of the present invention. [Figure 19] FIG. 13 is an external view of a rotary torsion testing device according to a seventh embodiment of the present invention. [Figure 20] FIG. 13 is an external view of a rotary torsion testing device according to an eighth embodiment of the present invention. [Figure 21] FIG. 13 is a top view of a tire wear testing device according to a ninth embodiment of the present invention. [Figure 22] FIG. 23 is an external view of a tire testing device according to a tenth embodiment of the present invention. [Diagram 23] FIG. 23 is an external view of a tire testing device according to a tenth embodiment of the present invention. [Figure 24] FIG. 19 is an external view of a power absorption durability testing device for an FR transmission according to an eleventh embodiment of the present invention. [Diagram 25] FIG. 23 is an external view of a power absorption durability testing device for a FF transmission according to a twelfth embodiment of the present invention. [Figure 26] FIG. 23 is a side view of a torsion test device according to a thirteenth embodiment of the present invention. [Figure 27] FIG. 23 is a side view of a first drive section according to a thirteenth embodiment of the present invention. [Figure 28] FIG. 23 is a plan view of a torsion test device according to a first modified example of the thirteenth embodiment of the present invention. [Figure 29] FIG. 23 is a plan view of a torsion test device according to a second modified example of the thirteenth embodiment of the present invention. [Diagram 30] FIG. 23 is a plan view of a torsion test device according to a third modified example of the thirteenth embodiment of the present invention. [Diagram 31] FIG. 23 is a side view of a torsion test device according to a fourteenth embodiment of the present invention. [Diagram 32] FIG. 23 is an enlarged view of a drive unit according to a fourteenth embodiment of the present invention. [Diagram 33] FIG. 23 is a top view of a vibration testing apparatus according to a fifteenth embodiment of the present invention. [Diagram 34] FIG. 23 is a side view of a first actuator according to a fifteenth embodiment of the present invention, as viewed from the Y-axis direction. [Diagram 35] FIG. 23 is a top view of a first actuator according to a fifteenth embodiment of the present invention. [Diagram 36] FIG. 23 is a side view of a table and a third actuator according to a fifteenth embodiment of the present invention, as viewed from the X-axis direction. [Figure 37] FIG. 23 is a side view of a table and a third actuator according to a fifteenth embodiment of the present invention, as viewed from the Y-axis direction. [Figure 38] FIG. 23 is a block diagram of a control system in a vibration testing apparatus according to a fifteenth embodiment of the present invention. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0018] Hereinafter, an embodiment of the present invention will be described with reference to the drawings.

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

[0020] The main body frame 150A1 is a substantially 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 body frame 150A1 so as to close the opening of the main body frame 150A1. The main body frame 150A1, the first bracket 150A3, and the second bracket 150A4 form a 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 a rotating force is applied to the drive shaft 150A2 by the interaction between a rotating magnetic field generated by the stator and the rotor provided on the drive shaft 150A2.

[0021] One end 150A2a (the right end in FIG. 1) of the drive shaft 150A2 penetrates the first bracket 150A3 and protrudes from the motor case to the outside to form the output shaft 150A2a. The other end 150A2b of the drive shaft 150A2 penetrates the second bracket 150A4 and protrudes from the motor case to the outside to form the second output shaft 150A2b. A rotary encoder (not shown) that detects the rotation of the other end 150A2b of the drive shaft 150A2 is built into the second bracket 150A4.

[0022] Further, a pair of tapped holes 150A3t and 150A4t for fixing the two-axis output servo motor 150A are provided on the lower surfaces of the first bracket 150A3 and the second bracket 150A4, respectively. In conventional servo motors, tapped holes for fixing extending parallel to the drive shaft are provided only on the mounting seat surface (right side surface in FIG. 1) of the bracket on the load side (side from which the output shaft protrudes). For applications other than precision machine testing, fixing only with the tapped holes provided on the mounting seat surface of the load side bracket is sufficient, but when using a high-output servo motor with a rated output of about 10 kW or more in a precision machine testing device (for example, a fatigue testing device or a vibration testing device) that applies a dynamic load with a high frequency of several tens of Hz (for example, 20 Hz) or more, the servo motor cannot be completely fixed in a direction perpendicular to the drive shaft only by fixing to the mounting seat surface of the bracket, and vibrations with a small amplitude of, for example, several μm to several tens of μm occur, causing a non-negligible error in the test results.

[0023] As a result of numerous vibration analyses and experiments, the inventors discovered that vibration noise can be significantly improved (for example, by about one order of magnitude) by adding two tapped holes for fixing on the underside of each bracket that extend in a direction perpendicular to the drive shaft. 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 can be reduced and more accurate mechanical testing can be performed.

[0024] In addition, the servo motor 150A has a high rated output of 37 kW and generates a large amount of heat during operation, so it is configured to dissipate the heat generated inside to the outside by water cooling. Two tube joints 150A6 are provided on the upper part of the main body 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 above-mentioned two-shaft output servo motor 150A and a servo motor 150B having one output shaft 150B2a are connected in series. Fig. 2 is a side view of the servo motor unit 150 according to the 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 from which the drive shaft 152 protrudes (the right side in FIG. 2) is referred to as the load side, and the opposite side is referred to as the anti-load side. The dual-axis output servo motor 150A and the 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 ) is a high-output, ultra-low inertia servo motor with a rated output of 37 kW.

[0027] The servomotor 150B includes a main body frame 150B1, a drive shaft 150B2, a load side bracket 150B3, a counter load side bracket 150B4, and a rotary encoder 150B5. The main body frame 150B1 and the load side bracket 150B3 are the same as the main body frame 150A1 and the first bracket 150A3 of the two-shaft output servomotor 150A, and two tube joints 150B6 are provided on the upper part of the main body frame 150B1 to which external piping for supplying and discharging cooling water is connected. The counter load side bracket 150B4 has a configuration substantially the same as the second bracket 150A4 of the two-shaft output servomotor 150A, but does not include a built-in rotary encoder. Instead, the rotary encoder 150B5 is externally attached to the counter load side bracket 150B4 as described later. Further, a pair of tapped holes 150B3t and 150B4t are provided in the lower surface of the load side bracket 150B3 and the anti-load side bracket 150B4, respectively.

[0028] One end 150B2a on the load side of the drive shaft 150B2 penetrates the load side bracket 150B3 and protrudes from the motor case to the outside to form the output shaft 150B2a. On the other hand, a rotary encoder 150B5 that detects the angular position of the drive shaft 150B2 is attached to the mounting seat surface (left side surface in FIG. 2) of the counter-load side bracket 150B4, and the other end 150B2b of the drive shaft 150B2 penetrates the counter-load side bracket 150B4 and is housed in the rotary encoder.

[0029] 2, the output shaft 152B2a of the servo motor 150B and the second output shaft 150A2b of the dual-shaft 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 dual-shaft output servo motor 150A are connected by a connecting flange 150D with a predetermined gap therebetween.

[0030] The connecting flange 150D has a cylindrical body 150D1 and two flange portions 150D2 extending radially outward from both axial ends of the body 150D1. Each flange portion 150D2 has a through hole for bolt fixing at a position corresponding to a tap hole provided in the mounting seat surface 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 a bolt.

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

[0032] For example, vibration tests and durability tests (rotational torsion tests) of power transmission devices require a large shaft torque that fluctuates at high speed (high frequency). In order to generate such a large torque that fluctuates at high frequency, a motor with a small rotor moment of inertia and large 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 extent, the rigidity of the rotor (rotating shaft) decreases, and the vibration of the rotor that is warped in a bow shape becomes prominent, making it impossible for the motor to operate normally. Therefore, in the conventional configuration in which the rotating shaft is supported only at both ends by a pair of bearings, there is a limit to increasing the capacity while maintaining a low moment of inertia.

[0033] In the servo motor unit 150 of this embodiment, the long rotor connected by the coupling 150C is supported by bearings at a total of four points, namely both ends in the longitudinal direction and two points near the connecting part. Therefore, even if the rotor is long, it is held with high rigidity and can operate stably. This makes it possible to generate large torque that fluctuates at high frequencies, which was not possible with conventional servo motors. For example, the servo motor unit 150 alone (unloaded state) can generate 30,000 rad / s 2 Angular accelerations of these magnitudes are achievable.

[0034] In addition, the servo motor unit 150 of this embodiment is configured to connect two servo motors (two motor cases and two rotating shafts), but as shown in Figure 3, it may also be configured so that one or more bearings are provided midway along the length of a pair of long motors and the drive shaft is supported at both ends and at one or more points midway.

[0035] Next, the configuration of the rotary torsion test apparatus 1 according to the first embodiment of the present invention will be described. Fig. 4 is a side view of the rotary torsion test apparatus 1 according to the first embodiment of the present invention. The rotary torsion test apparatus 1 is an apparatus for performing a rotary torsion test using an automobile clutch as a specimen T1, and can apply a set fixed or variable torque between the input shaft and output shaft (e.g., a clutch cover and a clutch disk) of the specimen T1 while rotating the specimen T1. The rotary torsion test apparatus 1 includes a stand 10 that supports each part of the rotary torsion test apparatus 1, a load-applying section 100 that rotates together with the test specimen T1 while applying a predetermined torque to the test specimen T1, bearing sections 20, 30 and 40 that support the load-applying section 100 for free rotation, slip ring sections 50 and 60 that electrically connect the inside and outside of the load-applying section 100, a rotary encoder 70 that detects the rotation speed of the load-applying section 100, an inverter motor 80 that rotates the load-applying section 100 in a set rotation direction and at a set rotation speed, a drive pulley 91 and a drive belt (timing belt) 92.

[0036] The frame 10 has a lower base plate 11 and an upper base plate 12 arranged horizontally one above the other, and a plurality of vertical support walls 13 connecting the lower base plate 11 and the upper base plate 12. A plurality of vibration-proof mounts 15 are attached to the underside of the lower base plate 11, and the frame 10 is placed on a flat floor F via the vibration-proof 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] 5 is a vertical cross-sectional view of the load applying section 100 of the rotary torsion test device 1. The load applying section 100 includes a stepped cylindrical casing 100a, a servo motor unit 150, a reducer 160, and a connecting shaft 170, which are attached inside the casing 100a, and a torque sensor 172. The casing 100a includes a motor housing section (body section) 110 in which the servo motor unit 150 is housed, a shaft section 120 rotatably supported by the bearing section 20, a shaft section 130 rotatably supported by the bearing section 30, and a shaft section 140 to which a slip ring 51 of a slip ring section 50 (FIG. 4) is attached. The motor housing section 110 and the shaft sections 120, 130, and 140 are each a substantially cylindrical member having a hollow section (or a stepped cylindrical member whose diameter changes stepwise in the axial direction). The motor housing 110 is a member with the largest outer diameter that houses the servo motor unit 150 in its hollow portion. One end of the motor housing 110 on the side of the test piece T1 (the right end in FIG. 5) is connected to the shaft portion 120, and the other end is connected to the shaft portion 130. Furthermore, the shaft portion 140 is connected to the end of the shaft portion 130 opposite the motor housing 110. The shaft portion 140 is rotatably supported by the bearing portion 40 at its tip end (the left end in FIG. 4).

[0038] 5, the servo motor unit 150 is fixed to the motor housing portion 110 by a plurality of fixed rods 111. The fixed rods 111 are screwed into tapped holes 150B3t provided in the load side bracket 150B3 of the servo motor 150B, tapped holes 150B4t provided in the anti-load side bracket 150B4, and tapped holes 150A3t provided in the first bracket 150A3 and tapped holes 150A4t provided in the second bracket 150A4 of the dual-shaft output servo motor 150A, respectively, as shown in FIG.

[0039] A drive shaft 152 of the servo motor unit 150 is connected to an input shaft of the reducer 160 via a coupling 154. A connecting shaft 170 is connected to an output shaft of the reducer 160. The reducer 160 includes a mounting flange 162, and the motor accommodating portion 110 and the shaft portion 120 are fastened together with a bolt (not shown) while the mounting flange 162 is sandwiched between the motor accommodating portion 110 and the shaft portion 120, whereby the reducer 160 is fixed to the casing 100a.

[0040] The shaft portion 120 is a substantially stepped cylindrical member, has a pulley portion 121 with a large outer diameter on the motor housing portion 110 side, and has a main shaft portion 122 rotatably supported by the bearing portion 20 on the specimen T1 side. As shown in FIG. 4, a drive belt 92 is wound around the outer circumferential surface of the pulley portion 121 and a drive pulley 91 attached to the drive shaft 81 of the inverter motor 80, and the drive force of the inverter motor 80 is transmitted to the pulley portion 121 by the drive belt 92, so that the load applying portion 100 rotates. In addition, the connection portion between the reducer 160 and the connection shaft 170 is housed in the pulley portion 121. By using the portion that needs to have a large outer diameter to house this connection portion as a pulley, a compact device structure is realized without increasing the number of parts.

[0041] A torque sensor 172 is attached to the tip end (the right end in FIG. 5) of the main shaft portion 122 of the shaft portion 120. One surface (the right side surface in FIG. 5) of the torque sensor 172 serves as a seat surface for mounting the input shaft (clutch cover) of the test piece T1, and the torque sensor 172 detects the torque applied to the test piece T1.

[0042] Bearings 123 and 124 are provided on the inner peripheral surface of the main shaft portion 122 of the shaft portion 120 near both ends in the axial direction. The connecting shaft 170 is supported by the bearings 123 and 124 so as to be rotatable within the shaft portion 120. The torque sensor 172 is formed in a substantially cylindrical shape having a hollow portion, and the tip portion (the right end portion in FIG. 5) of the connecting shaft 170 penetrates the hollow portion of the torque sensor 172 and protrudes to the outside. The tip portion protruding from the torque sensor 172 is inserted into and fixed to a shaft hole of a clutch disc (clutch hub) which is the output shaft of the test piece T1. That is, by driving the connecting shaft 170 to rotate relative to the casing 100a of the load applying portion 100 by the servo motor unit 150, a set dynamic or static torque can be applied between the input shaft (clutch cover) of the test piece T1 fixed to the casing 100a and the output shaft (clutch disc) of the test piece T1 fixed to the connecting shaft 170.

[0043] As shown in FIG. 4, a rotary encoder 70 for detecting the number of rotations of the load applying part 100 is disposed near the end part of the shaft part 130 (the left end part in FIG. 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 (FIG. 5) that supplies a 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 hollow sections formed in the shaft sections 130 and 140.

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

[0046] A slip ring (not shown) of the slip ring unit 60 is attached to the tip end (left end in FIG. 4) of the shaft unit 140. A communication line 150W' (FIG. 5) extending from the servo motor unit 150 is connected to the slip ring of the slip ring unit 60, and signals such as a torque sensor 172 and a rotary encoder 150B5 (FIG. 2) built into the servo motor unit 150 are output to the outside via the slip ring unit 60. When a large current such as a driving current of a large capacity motor flows through the slip ring, a large electromagnetic noise is likely to be generated due to discharge. In addition, since the slip ring is not sufficiently shielded, it is likely to be interfered with by electromagnetic noise. As described above, the communication line 150W' through which a weak current flows and the power line 150W through which a large current flows are connected to external wiring using separate slip rings arranged at a certain distance from each other, so that the intrusion of noise into the communication signal is effectively prevented. In this embodiment, the slip ring portion 60 is provided on the surface of the bearing portion 40 opposite to the side of the slip ring portion 50. With this configuration, the bearing portion 40 also has the effect of shielding the slip ring portion 60 from electromagnetic noise generated in the slip ring portion 50.

[0047] Next, the control system of the rotary torsion test apparatus 1 will be described. Fig. 6 is a block diagram showing a schematic configuration of the control system of the rotary torsion test apparatus 1. The rotary torsion test apparatus 1 includes a control unit C1 for controlling the entire rotary torsion test apparatus 1, a setting unit 370 for setting test conditions, a waveform generating unit 320 for calculating a waveform of the drive amount of the servo motor unit 150 based on the set test conditions (such as the waveform of the torque and torsion angle applied to the test specimen) and outputting the waveform to the control unit C1, a servo motor driving unit 330 for generating a drive current of the servo motor unit 150 based on the control of the control unit C1, an inverter motor driving unit 340 for generating a drive current of the inverter motor 80 based on the control of the control unit C1, a torque measuring unit 350 for calculating the torque applied to the test specimen based on a signal from the torque sensor 172, and a rotation speed measuring unit 360 for calculating the rotation speed of the load applying unit 100 based on a signal from the rotary encoder 70.

[0048] The setting unit 370 includes a user input interface such as a touch panel (not shown), a removable recording medium reader such as a CD-ROM drive, and an interface such as a GPIB (General Purpose Interface Bus) or a USB (Universal The test device 1 is provided with an external input interface such as a USB Serial Bus and a network interface. The setting unit 370 sets test conditions based on user input received via a user input interface, data read from a removable recording medium, data input from an external device (e.g., a function generator) via an external input interface, and / or data acquired from a server via a network interface. The rotary torsion test device 1 of this embodiment supports two control methods: a displacement control that controls the torsion applied to the test specimen T1 based on the torsion angle applied to the test specimen T1 (i.e., the driving amount of the servo motor unit 150 detected by the rotary encoder 150B5 built in the servo motor unit 150), and a torque control that controls based on the torque applied to the test specimen T1 (i.e., detected by the torque sensor 172). The setting unit 370 can set which control method is used for control.

[0049] The control unit C1 commands the inverter motor driving unit 340 to rotate the inverter motor 80 based on the set value of the rotation speed of the specimen T1 acquired from the setting unit 370. Also, the control unit C1 commands the servo motor driving unit 330 to drive the servo motor unit 150 based on the waveform data of the drive amount of the servo motor unit 150 acquired from the waveform generating unit 320.

[0050] 6, the measured value of torque calculated by the torque measurement unit 350 based on the signal of the torque sensor 172 is sent to the control unit C1 and the waveform generating unit 320. Also, the signal of the built-in rotary encoder built into the servo motor unit 150 is sent to the control unit C1, the waveform generating unit 320, and the servo motor driving unit 330. The waveform generating unit 320 calculates the measured value of the rotation speed of the servo motor unit 150 from the signal of the built-in rotary encoder that detects the rotation angle of the driving shaft 152 of the servo motor unit 150. In the case of torque control, the waveform generating unit 320 compares the set value of torque (the driving amount of the servo motor unit 150 in the case of displacement control) with the measured value, and corrects the set value of the driving amount of the servo motor unit 150 sent to the control unit C1 so that the two match.

[0051] Furthermore, the measured value of the rotation speed of the load applying part 100 calculated by the rotation speed measuring unit 360 based on the signal of the rotary encoder 70 is sent to the control unit C1. The control unit C1 compares the set value of the rotation speed of the load applying part 100 with the measured value, and feedback controls the frequency of the drive current sent to the inverter motor 80 so that the two values ​​match.

[0052] In addition, the servo motor drive unit 330 compares a 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 feedback controls the drive current sent to the servo motor unit 150 so that the drive amount approaches the target value.

[0053] The control unit C1 also includes a hard disk drive (not shown) for storing test data, and records the measured data of the rotation speed of the test specimen T1, the torsion angle (the rotation angle of the servo motor unit 150) applied to the test specimen T1, and the torsion load on the hard disk drive. The time change of each measured value is recorded over the entire period from the start to the end of the test. With the configuration of the first embodiment described above, a rotation torsion test is performed using an automobile clutch as the test specimen T1.

[0054] In the above-mentioned rotational torsion test device 1, the output of the inverter motor 80 for controlling the rotational speed and the output of the servo motor unit 150 for controlling the torque are combined, and the rotational speed and the torque can be controlled independently and with high precision. In particular, by newly adopting the servo motor unit 150 in which a plurality of ultra-low inertia servo motors are connected in series, it is possible to control a large torque that fluctuates with a high angular jerk (angular jerk), and the output of an automobile engine (particularly, the torque vibration of a reciprocating engine) can be accurately reproduced. In addition, by using the servo motor unit 150, the responsiveness of the torque control is improved, and a response time of 3 ms or less is achieved. A rotational drive device having such a configuration can be used as a power source for various devices, not limited to the rotational torsion test device. In particular, in a test device for automobiles (or automobile parts), it can be used as a power simulator (simulated engine) that can output power simulating various types of engine output. In addition, since the torque generated by the servo motor unit 150 is controlled with high precision, it has extremely high reproducibility and does not have individual differences. This makes it possible to apply a more uniform load than conventional tests using an actual engine, enabling tests with higher reproducibility.

[0055] (Modification of the first embodiment) 7 and 8 are external views of dynamic simulators 1a and 1b which are partially modified versions of the rotary torsion testing device 1 according to the first embodiment of the present invention described above.

[0056] The power simulator 1a shown in FIG. 7 is different from the above-mentioned rotary torsion test device 1 in that it includes a bearing unit 1020, a slip ring 1401, and an attachment unit 173. The bearing unit 1020 has the same configuration as the bearing unit 1020 of the second embodiment described later, and includes a torque sensor that detects the torque of the connecting shaft 170 (the connecting shaft 1170 in the second embodiment). The slip ring 1401 is attached to the bearing unit 1020, and extracts a signal output from the torque sensor included in the bearing unit 1020 to the outside. The attachment unit 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 tests of engine accessories (for example, damper pulleys, alternators, balance shafts, starter motors, ring gears, water pumps, oil pumps, chains, timing belts, couplings, VCTs), power transmission devices, tires, etc.

[0057] Furthermore, in the above-described rotary torsion test device 1 and power simulator 1a, the inverter motor 80 is disposed on the lower base plate 11, and the load application unit 100 is disposed on the upper base plate 12, forming a two-tier structure. However, as in the power simulator 1b shown in FIG. 8, the inverter motor 80 and the load application unit 100 may be disposed on the same base plate 10X in a single-tier structure. The two-tier structure is effective in reducing the installation area. Furthermore, the single-tier structure is advantageous in reducing costs due to its simple structure, and is also advantageous in improving the rigidity of the base (i.e., vibration resistance and load resistance).

[0058] Next, a specific example of an engine accessory durability test device using the power simulator 1a will be described. The test device 100E described below is a starter motor test device that performs a durability test by applying a rotational driving force simulating an engine load generated by the power simulator 1a to a flywheel ring gear T1 and a starter motor T2 as test specimens. The test device 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] Fig. 9 is a side view of the test device 100E, and Fig. 10 is an enlarged view of the vicinity of the test specimen (ring gear T1, starter motor T2).

[0060] As shown in Figs. 9 and 10, the test device 100E is a power simulator 1a to which a support S for holding a specimen is added. That is, the test device 100E includes an inverter motor 80 attached to a lower base plate 11 of a stand 10, and a load applying unit 100 rotatably supported by bearings 1020, 30, and 40 attached to an upper base plate 12. The load applying unit 100 is driven to rotate by the inverter motor 80. A servo motor unit 150 and a reducer are built into the load applying unit 100, and an output shaft of the servo motor unit 150 is connected to a connecting shaft 170 protruding outside the load applying unit 100 via the reducer. The connecting shaft 170 is arranged coaxially with the rotating shaft of the load applying unit 100, and the rotation of the connecting shaft 170 is the rotation of the load applying unit 100 by the inverter motor 80 plus the rotation of the servo motor unit 150. The engine speed is reproduced by the inverter motor 80, and the high-speed varying torque (high angular acceleration, high angular jerk (angular jerk)) of the engine is reproduced by the servo motor unit 150.

[0061] An attachment portion 173 for attaching a ring gear T1 is attached to the tip of the connecting shaft 170 of the load applying portion 100. In addition, a support portion S for supporting a starter motor T2 is attached to the upper base plate 12 of the stand 10. When the ring gear T1 is attached to the attachment portion 173 and the starter motor T2 is attached to the support portion S, the ring gear T1 and the pinion gear of the starter motor T2 are engaged with each other. In this state, the power simulator 1a of the testing device 100E is driven to apply a rotation simulating the rotation of an engine to the ring gear T1 and the starter motor T2, thereby performing a test.

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

[0063] As shown in FIG. 11, the rotary torsion test apparatus 1000 includes four bases 1011, 1012, 1013, and 1014 that support the various components of the rotary torsion test apparatus 1000, a load application unit 1100 that applies a predetermined torque between both ends of the test piece T2 while rotating together with the test piece 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 wiring inside and outside the load application unit 1100, and a rotation speed controller 1030 that controls the rotation speed of the load application unit 1100. The test specimen T2 is provided with a rotary encoder 1070 for detecting the rotational speed of the load applying unit 1100 and an inverter motor 1080 for rotating the load applying unit 1100 and one end of the test specimen T2 (the right end in FIG. 11) in a set rotational direction and rotational speed, a driving force transmission unit 1190 (a driving pulley 1191, a driving belt (timing belt) 1192, and a driven pulley 1193) for transmitting the driving force of the inverter motor 1080 to the load applying unit 1100, and a driving force transmission unit 1200 for transmitting the driving force of the inverter motor 1080 to the one end of the test specimen T2. ​​The driving force transmission unit 1200 is provided with a bearing unit 1210, a driving shaft 1212, an intermediate shaft 1220, a bearing unit 1230, a driving shaft 1232, a driving pulley 1234, a bearing unit 1240, a driving shaft 1242, a driven pulley 1244, a driving belt (timing belt) 1250, and a workpiece mounting unit 1280.

[0064] The bearings 1020, 1030, 1040, the slip rings 1050, 1060, the rotary encoder 1070, the inverter motor 1080, and the drive pulley 1091 in the rotary torsion test device 1000 are configured similarly to the bearings 20, 30, 40, the slip rings 50, 60, the rotary encoder 70, the inverter motor 80, and the drive pulley 91 in the rotary torsion test device 1 of the first embodiment, respectively. The load applying unit 1100 has the same configuration as the load applying unit 100 of the first embodiment, except for the shaft 1120, the connecting shaft 1170, the workpiece mounting unit 1180, and the slip ring unit 1400, which will be described later. The drive belt 1192 is different from the drive belt 92 of the first embodiment in that it is hung on the driven pulley 1193 on the driven side, but the other configurations are the same as the drive belt 92. In the following description of the second embodiment, the same or similar components as those in the first embodiment are denoted by the same or similar reference numerals, detailed description is omitted, and differences in configuration from the first embodiment are mainly described.

[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 unit 1210 are fixed on the base 1011. The bearing units 1020, 1030, and 1040 that support the load application unit 1100 and the support frame 1402 of the slip ring unit 1400 are fixed on the base 1012. The bearing unit 1230 is fixed to the base 1013, and the bearing unit 1240 is fixed to the base 1014. The bases 1013 and 1014 can be moved in the axial direction of the bearing unit 1230 or 1240 depending on the length of the test piece T1 by loosening the fixing bolts.

[0066] The connecting shaft 1170 of the load applying part 1100 protrudes outward from the tip end (the right end in FIG. 13) of the shaft part 1120, and a work mounting part (flange joint) 1180 is fixed to the tip end (the right end part in FIG. 13) of the connecting shaft 1170. A slip ring 1401 having a plurality of electrode rings is attached to the axial center of the part of the connecting shaft 1170 protruding from the shaft part 1120.

[0067] As shown in FIG. 13, a ring-shaped narrowed portion 1172 having a small outer diameter is formed in the portion of the connecting shaft 1170 accommodated in the shaft portion 1120, and a strain gauge 1174 is attached to the peripheral surface of the narrowed portion 1172. The connecting shaft 1170 is a cylindrical member having a hollow portion (not shown) penetrating the central axis, and the narrowed portion 1172 has an insertion hole (not shown) communicating with the hollow portion. The leads (not shown) of the strain gauge 1174 are passed through the above-mentioned insertion hole and hollow portion formed in the connecting shaft 1170 and connected to each electrode ring of the slip ring 1401. Instead of the hollow portion and the insertion hole, a wiring groove extending from the narrowed portion 1172 to the slip ring 1401 may be provided on the peripheral surface of the connecting shaft 1170, and the leads of the strain gauge 1174 may be wired to the slip ring 1401 through the wiring groove.

[0068] A brush unit 1403 fixed on a support frame 1402 is disposed below the slip ring 1401. The brush unit 1403 has a plurality of brushes disposed opposite each other so as to be in contact with each electrode ring of the slip ring 1401. The terminals of each brush are connected to a torque measurement unit 1350 (described later) by wires (not shown).

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

[0070] The driving force of the inverter motor 1080 is transmitted to the workpiece mounting part 1280 via the driving force transmission part 1200 (i.e., the driving shaft 1212, the intermediate shaft 1220, the driving shaft 1232, the driving pulley 1234, the driving belt 1250, the driven pulley 1244, and the driving shaft 1242) described above, causing the workpiece mounting part 1280 to rotate in a set rotation direction and at a set number of rotations. At the same time, the driving force of the inverter motor 1080 is transmitted to the load applying part 1100 via the driving force transmission part 1190 (i.e., the driving pulley 1191, the driving belt 1192, and the driven pulley 1193), causing the load applying part 1100 and the workpiece mounting part 1280 to rotate synchronously (i.e., always at the same number of rotations and in the same phase).

[0071] Third embodiment In the second embodiment described above, the drive shaft 1212 and the load applying section 1100, and the drive shaft 1232 and the drive shaft 1242, which are arranged in parallel to each other, are connected by the 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 device 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] Fig. 14(a) is a top view of a torsion test apparatus according to a third embodiment of the present invention. Fig. 14(b) is a side view of the torsion test apparatus according to this embodiment. As shown in Fig. 14, the torsion test apparatus 100 of this embodiment has a workpiece rotating servomotor 121, a torque imparting unit 130, a first gear box 141, and a second gear box 142 fixed on a base 110.

[0073] The first gear box 141 has four shaft connecting portions 141a1, 141a2, 141b1, and 141b2, while the second gear box 142 has two shaft connecting portions 142a and 142b.

[0074] A driving pulley 122 is attached to the output shaft 121a of the workpiece rotating servomotor 121. Also, a shaft 123a of a driven pulley 123 is attached to a shaft connection part 141a1 of the first gear box 141. Also, an endless belt 124 is hung between the driving pulley 122 and the driven pulley 123, and by driving the workpiece rotating servomotor 121, it is possible to rotate the driven pulley 123 at a desired rotational speed.

[0075] The shaft connecting portions 141b1 and 141b2 are connected to the torque applying unit 130. The configuration of the torque applying unit 130 will be described below.

[0076] FIG. 15 is a side cross-sectional view of the torque applying unit 130 and the first gear box 141 of this embodiment. The torque applying unit 130 includes a casing 131, a torque applying servo motor unit 132 fixed in the casing 131, and a reducer 133. The torque applying 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 side (right side in the figure) of the casing 131. The tubular portion 131a is inserted into the first gear box 141 via a shaft connection portion 141b1 and is supported rotatably in the first gear box 141. A gear 141b3 is attached to the tubular portion 131a.

[0077] The reducer 133 has an input shaft 133a and an output shaft 133b, and reduces the speed of the rotational motion input to the input shaft 133a and outputs it to the output shaft 133b. The input shaft 133a of the reducer 133 is connected to the output shaft 132a of the torque application servo motor unit 132 by a coupling 134. The output shaft 133b of the reducer 133 is rotatably supported inside the tubular portion 131a of the casing 131 and protrudes from the tip end of the tubular portion 131a. The output shaft 133b of the reducer 133 protruding from the tubular portion 131a is connected to the shaft connection portion 141b2 of the first gear box 141.

[0078] 14, the output shaft 133b of the reducer 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 gear box 142 via a torque sensor 160.

[0079] An output shaft W2b of the transmission unit W2 is connected to a shaft connection portion 142a of the second gear box 142 via an intermediate shaft 143. An input shaft W2a of the transmission unit W2 is connected to a shaft connection portion 141a2 of the first gear box 141 via a coupling 152.

[0080] Here, the shaft 123a of the driven pulley 123 attached to the shaft connection part 141a1 of the first gear box 141 and the shaft attached to the shaft connection part 141a2 are connected via a coupling 153 inside the first gear box 141, and are configured so that the two rotate together. In addition, a gear 141a3 is attached to the shaft 123a of the driven pulley 123 attached to the shaft connection part 141a1. A gear 141b3 is attached to the tubular part 131a connected to the shaft connection part 141b1 inside the first gear box 141. As shown in FIG. 14(a), the gear 141a3 and the gear 141b3 are engaged with each other via an intermediate gear 141i, and a rotational motion can be transmitted between the shaft connected to the shaft connection parts 141a1 and 141a2 and the shaft connected to the shaft connection part 141b1. Since the intermediate gear 141i is interposed between the gears 141a3 and 141b3, the driven pulley 123, the intermediate shaft 143, and the casing 131 of the torque applying unit 130 rotate in the same direction.

[0081] A gear 142a1 is attached to the shaft portion (one end of the intermediate shaft 143) connected to the shaft connection portion 142a. A gear 142b1 is connected to the shaft portion connected to the shaft connection portion 142b. The gears 142a1 and 142b1 mesh with each other through an intermediate gear 142i inside the second gear box 142, and rotational motion can be transmitted between the shaft connected to the shaft connection portion 142a and the shaft connected to the shaft connection portion 142b. Since the intermediate gear 142i is interposed between the gears 142a1 and 142b1, the shaft connected to the shaft connection portion 142a and the shaft connected to the shaft connection portion 142b rotate in the same direction.

[0082] Therefore, in this embodiment, when the workpiece rotating servomotor 121 (FIG. 14) is driven, the driven pulley 123 and the casing 131 (FIG. 15) connected to the driven pulley 123 via a gear are rotated. As described above, the torque applying servomotor unit 132 is fixed to the casing 131, so the casing 131 and the torque applying servomotor rotate together. Therefore, when the torque applying servomotor unit 132 is driven while the casing 131 is rotating, the output shaft 133b of the reducer 133 rotates at a speed obtained by adding the rotation speed of the casing 131 and the rotation speed of the output shaft 133b by the torque applying servomotor unit 132.

[0083] The transmission unit W2 is of the same type (same reduction ratio) as the transmission unit W1. In addition, the gear ratios of the gear boxes 141 and 142 are both 1:1. Therefore, the rotation speeds of the shafts connected to the shaft connecting parts 141a2 and 141b2 of the first gear box 141 are approximately equal. Note that the transmission unit W2 is a kind of dummy work used to adjust the rotation speeds of the shafts connected to the shaft connecting parts 141a2 and 141b2 as described above, and is not the subject of the torsion test.

[0084] In this embodiment, for example, by driving the workpiece rotating servo motor 121 at a constant speed and reciprocatingly driving the output shaft 132a by the torque applying servo motor unit 132 (Figure 15), it is possible to apply a periodically varying 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. Fig. 16 is a top view of a torsion test apparatus according to the fourth embodiment of the present invention. As shown in Fig. 16, the torsion test apparatus 100A of this embodiment is the same as the torsion test apparatus 100 of the third embodiment, except that a dummy workpiece is not used and the coupling 152 and the shaft connection part 142a of the second gear box 142 are directly connected by the relay shaft 143A. In the following description of the fourth embodiment, elements having the same or similar functions as those of the third embodiment are given the same or similar reference numerals, and duplicated descriptions are omitted.

[0086] In this embodiment, the rotation speed of the intermediate shaft 143A (i.e., the rotation speed of the casing 131 of the torque imparting unit 130) is different from the rotation speed of the shaft connected to the shaft connection portion 141b2 of the first gear box 141 (i.e., the rotation speed of the input shaft W1a of the transmission unit W1). Therefore, in this embodiment, the torque imparting servo motor unit 132 (FIG. 15) of the torque imparting unit 130 is rotationally driven to compensate for the change in the rotation speed of the input and output shafts of the transmission unit W1. For example, if a torsion test is performed with a reduction ratio of 1 / 3.5 for the transmission unit W1 and with the input shaft W1a rotating at a speed of 4000 rpm and the output shaft W1b rotating at a speed of 1143 rpm, the rotation speed of the workpiece rotating servo motor 121 can be set so as to impart a rotation of 1143 rpm to the casing 131 of the torque imparting unit 130, and the rotation speed of the torque imparting servo motor unit 132 can be set so that the relative rotation speed of the output shaft 133b of the reducer 133 to the casing 131 is 2857 rpm, thereby making the rotation speed of the input shaft W1a of the transmission unit W1 4000 rpm.

[0087] In this manner, in this embodiment, a torsion test of the transmission unit W1 can be performed without using a dummy workpiece while performing power circulation.

[0088] In addition, in this embodiment, since the workpiece is rotated and torque is applied by a highly responsive servo motor, it is also possible to change the gear ratio of the transmission unit W1 during the torsion test. That is, in this embodiment, the rotation speed of the torque application servo motor unit 131 can be suddenly changed in synchronization with the change in the rotation speed of the output shaft W1b caused by the change in the gear ratio of the transmission unit W1, so that even if the gear ratio of the transmission unit W1 is changed, the gears in the gear boxes 141 and 142 and the transmission unit W1 will not be damaged due to excessive load.

[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 a torsion test on other types of workpieces. The torsion test device according to the fifth embodiment of the present invention described below performs a torsion test on the entire power transmission system of a FR vehicle as the workpiece.

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

[0091] In the torsion test apparatus 100B of this embodiment, since there are two systems (DG1a, DG1b) of output shafts of the differential gear DG1, two systems of second gear boxes (142B1, 142B2) and relay shafts (143B1, 143B2) are provided for returning the output of the differential gear DG1 to the first gear box 141B. Specifically, the output shafts DG1a, DG1b of the differential gear DG1 are connected to relay shafts 143B1, 143B2 via second gear boxes 142B1, 142B2, respectively.

[0092] The first gear box 141B also has shaft connecting parts 141Bb1 and 141Bb2 (having the same function as the shaft connecting parts 141b1 and 141b2 in the third embodiment) to which the tubular part 131a of the casing 131 of the torque applying unit 130 and the input shaft TR1a of the transmission unit TR1 are respectively attached, shaft connecting parts 141Ba1 and 141Ba2 to which the output shaft 121a of the workpiece rotating servo motor 121 and the relay shaft 143B1 are connected, and a shaft connecting part 143Bc to which the relay shaft 143B2 is connected. The output shaft 121a of the workpiece rotating servo motor 121 and the relay shaft 143B1 are connected via a coupling 153B arranged in the first gear box 141. The input shaft TR1a of the transmission unit TR1 and the output shaft 133b of the reducer 133 of the torque applying unit 130 are connected via a coupling 151B arranged in the first gear box 141.

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

[0094] In this embodiment, as in the fourth embodiment, the rotation speed of the input shaft TR1a of the transmission unit TR1 is different from the rotation speed of the intermediate shafts 143B1 and 143B2, so that the rotation speed of the torque-imparting motor 131 (FIG. 15) is controlled to compensate for the difference in the rotation speed.

[0095] Sixth embodiment In addition, in the configuration of the present invention, it is also possible to use a power transmission system for a FF vehicle as the workpiece. The torsion test device according to the sixth embodiment of the present invention described below is used to perform a torsion test on the power transmission system of a FF vehicle.

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

[0097] 18, the power transmission system W4 is a power transmission system for a horizontally 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 gear box 141C, and only the other output shaft DG2b is connected to the relay shaft 143C via the second gear box 142C.

[0098] The first gear box 141C of this embodiment has shaft connection parts 141Cb1 and 141Cb2 to which the tubular part 131a of the casing 131 of the torque imparting unit 130 and the input shaft TR2a of the transmission unit TR2 are respectively attached, shaft connection parts 141Ca1 and 141Ca2 to which the output shaft 121a of the workpiece rotating servo motor 121 and the output shaft DG2a of the differential gear DG2 are connected, and a shaft connection part 143Cc to which the intermediate shaft 143C is connected, as in the fifth embodiment. The output shaft 121a of the workpiece rotating servo motor 121 and the output shaft DG2a of the differential gear DG2 are connected by a coupling 153C arranged in the first gear box 141C. In addition, the output shaft 133b of the reducer 133 of the torque imparting unit 130 and the input shaft TR2a of the transmission unit TR2 are connected by a coupling 151C arranged in the first gear box 141C.

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

[0100] In this embodiment, similarly to the fourth and fifth embodiments, the rotation speed of the input shaft TR2a of the transmission unit TR2 differs from the rotation speed of the output shaft DG2a of the differential gear DG2 and the intermediate shaft 143C, and therefore the rotation speed of the torque-imparting motor 131 (FIG. 15) is controlled to compensate for the difference in the rotation speed.

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

[0102] In the torsion test apparatus 100B of this embodiment, since there are two systems (DG1a, DG1b) of output shafts of the differential gear DG1, two systems of second gear boxes (142B1, 142B2), bevel gear boxes (144B1, 144B2) and relay shafts (143B1, 143B2) are provided to return the output of the differential gear DG1 to the first gear box 141B. Specifically, the output shafts DG1a, DG1b of the differential gear DG1 are connected to relay shafts 143B1, 143B2 via second gear boxes 142B1, 142B2 and bevel gear boxes 144B1, 144B2, respectively.

[0103] The first gear box 141B includes a gear 141Bb and gears 141Ba and 141Bc which engage with the gear 141Bb. A tubular portion of a casing of the torque applying unit 130 is connected to the gear 141Bb. Intermediate shafts 143B1 and 143B2 are connected to the 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 the input shaft DG1c of the differential gear DG1 are connected to the gear boxes 142B1, 142B2 and the shafts of the torque applying unit 130 via torque sensors 172a, 172b and 172c, respectively. The torque sensors 172a, 172b and 172c are configured such that a shaft 1170 having a strain gauge 1174 attached to a narrowed portion 1172, as shown in Fig. 13 (second embodiment), is supported by a bearing portion 1020 (directly without via a shaft portion 1120).

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

[0106] Eighth embodiment The present invention can also be applied to a test device for a power transmission device for a front-wheel drive vehicle. The torsion test device according to the eighth embodiment of the present invention described below is a power circulation type test device for performing a rotational torsion test on the power transmission system of a front-wheel drive vehicle.

[0107] Fig. 20 is an external view of a torsion test apparatus 100C according to an eighth embodiment of the present invention. As shown in Fig. 20, the torsion test apparatus 100C of this embodiment performs a rotational torsion test on a transmission unit TR for a FF vehicle.

[0108] As shown in FIG. 20, the input shaft TRa and the output shafts TRb and TRc of the transmission unit TR are connected to the first gear box 141C via the torque sensors 172b, 172b, and 172c, respectively, without being decelerated. The input shaft TRa and the 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 gear box 141C, and the other output shaft TRc is connected to the first gear box 141C via the second gear box 142C and the relay shaft 143C arranged substantially parallel to the output shaft TRc. That is, the driving force of the output shaft TRc is folded back 180° by the second gear box 142C, and then transmitted to the first gear box 141C by the relay shaft 143C.

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

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

[0111] The third to eighth embodiments of the present invention described above are examples in which the present invention is applied to a power circulation type torsion test device that uses a power transmission system such as a transmission unit as a workpiece. However, the present invention is not limited to the above configuration. As in the ninth and tenth embodiments of the present invention described below, the present invention can also be applied to various tests of tires.

[0112] Ninth embodiment 21 is a top view of a tire wear testing apparatus 100D according to a ninth embodiment of the present invention. The tire wear testing apparatus 100D has a power circulation mechanism having a similar configuration to that of the third embodiment described above.

[0113] The first gear box 141D has four shaft connecting portions 141Da1, 141Da2, 141Db1, and 141Db2, while the second gear box 142D has two shaft connecting portions 142Da and 142Db.

[0114] In this embodiment, both ends of a shaft 145 serving as a rotating shaft of a rotating drum DR serving as a simulated road surface are connected to a shaft connection part 141Da2 of a first gear box 141D and a shaft connection part 142Da of a second gear box 142D, respectively. Also, both ends of a shaft 144 serving as a rotating shaft of a tire T serving as a test object are connected to a shaft connection part 141Db2 of a first gear box 141D and a shaft connection part 142Db of a second gear box 142D, respectively.

[0115] As in the second embodiment, the rotation of the output shaft 121a of the workpiece rotating servo motor 121 for driving the tire T and the rotating drum DR drives and rotates the shaft 123a of the driven pulley 123 via a belt mechanism composed of a drive pulley 122, a driven pulley 123, and an endless belt 124. The shaft 123a is connected to a shaft connection portion 141a of a first gear box 141D.

[0116] A tubular portion 131a of a casing 131 of the torque applying unit 130 is connected to the shaft connection portion 141Db1 of the first gear box 141D. In addition, an output shaft 133b of the reducer 133 of the torque applying unit 130 is coupled to one end of a shaft 144 for the tire T via a coupling 151D arranged inside the first gear box 141D.

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

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

[0119] Further, shaft 145 attached to shaft connecting portion 142Da of second gear box 142 and shaft 144 attached to shaft connecting portion 142Db are each connected to different gears provided inside second gear box 142. These gears mesh with each other inside second gear box 142, and the rotation of shaft 144 is transmitted to shaft 145 by second gear box 142.

[0120] As configured as described above, it is possible to rotate the rotating drum DR and the tire T while circulating power by driving the rotation servo motor 121. Note that, as shown in Fig. 21, in this embodiment, since the rotating drum DR and the tire T have different diameters, the gear ratio in the first gear box 141D and the second gear box 142D is set to a value corresponding to the ratio of the diameters of the rotating drum DR and the tire T.

[0121] In the tire wear testing device configured as described above, the tire T is set on the shaft 144 and the rotation servo motor 121 is driven to rotate the tire T and the rotating drum DR. In this state, the torque application servo motor unit 131 (FIG. 2) of the torque application unit 130 is driven to apply torque in the forward and reverse directions to the tire T, thereby making it possible to perform a wear test that simulates the acceleration and deceleration of an automobile.

[0122] Tenth embodiment Another example in which the present invention is applied to a tire test will be described. The tire testing apparatus according to the tenth embodiment of the present invention described below is an apparatus for performing abrasion tests, durability tests, running stability tests, etc. on tires.

[0123] 22 and 23 are perspective views of a tire testing apparatus 100D according to a tenth embodiment of the present invention, as seen from different directions. The tire testing apparatus 100D of this embodiment includes a rotating drum 10 having a simulated road surface formed on its outer circumferential surface, an inverter motor 80 that rotates and drives the rotating drum 10 and a casing of a torque applying unit 130, an alignment control mechanism 160, and a torque applying unit 130 that applies torque to a tire T rotatably supported by the alignment control mechanism 160. A servo motor unit 150 having the same configuration as in the first embodiment is built into the torque applying unit 130.

[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. The 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. The pulley 12c is connected to a pulley 12d by a drive belt. The pulley 12d is fixed coaxially to the pulley 12e, and is rotatably supported together with the pulley 12e by a bearing 11c (FIG. 27). The pulley 12e is also connected to a tubular portion of a casing of the torque applying unit 130 by a drive belt.

[0125] Further, the drive shaft of the servo motor unit 150 built in the torque applying unit 130 is connected, via the intermediate shaft 14 and a flexible coupling, to a wheel of an alignment control mechanism 160 on which the tire T is mounted.

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

[0127] The alignment control mechanism 160 of this embodiment is a mechanism that supports the tire T, which is a specimen, in a state where 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 with respect to the simulated road surface and the tire load (ground pressure) 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 line 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 direction of the rotation axis.

[0128] By setting the tire T in the tire testing apparatus 100D having the above-described configuration 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 applying unit 130 to apply a driving force or a braking force to the tire T, it becomes possible to perform a tire wear test, a durability test, a running stability test, and the like, which simulate an actual running condition.

[0129] Eleventh embodiment Next, a test device for a power absorption type power transmission device using a power simulator according to an embodiment of the present invention will be described.

[0130] FIG. 24 is an external view of a power absorption durability testing device 100F for an FR transmission according to an eleventh embodiment of the present invention.

[0131] The test device 100F includes a power simulator 100X having an inverter motor 80 and a load applying section 100 incorporating a servo motor unit 150, a support section S for supporting a case of a front-rear transmission T as a test specimen, torque sensors 172a and 172b, and two power absorbing servo motors 90A and 90B. The input shaft of the front-rear transmission T is connected to the output shaft of the load applying section 100 via the torque sensor 172a. The output shaft To of the front-rear transmission T is connected to the pulley section 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 unit 180 is connected to two power absorbing servomotors 90A and 90B by two drive belts. The two power absorbing servomotors 90A and 90B are driven synchronously to apply a load to the output shaft To of the FR transmission T.

[0133] Twelfth embodiment FIG. 25 is an external view of a power absorption durability testing device 100G for a FF transmission according to the twelfth embodiment of the present invention.

[0134] The FF transmission TR, which is a specimen, has 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 applying unit 100 via a torque sensor 172a. The output shaft TRb (TRc) of the FF transmission TR is connected to a power absorbing servo motor 90B (90C) via a torque sensor 172b (172c), a pulley unit 180b (180c), and a drive belt. The power absorbing servo motor 90B (90C) applies a load to the output shaft TRb (TRc) of the FF transmission TR. The torque sensors 172a, 172b, and 172c have the same configuration as the torque sensors 172a, 172b, and 172c of the seventh embodiment.

[0135] Thirteenth embodiment Next, a low-speed rotational torsion test apparatus according to the thirteenth embodiment of the present invention will be described. FIG. 26 is a side view of a torsion test apparatus 3100 according to the thirteenth embodiment of the present invention. The torsion test apparatus 3100 of this embodiment is an apparatus for performing a rotational torsion test on a specimen T1 (for example, a transmission unit for a FR vehicle) having two rotating shafts. That is, the torsion test apparatus 3100 rotates the two rotating shafts of the specimen T1 while applying a torque by giving a phase difference to the rotation of the two rotating shafts while rotating the two rotating shafts synchronously. The torsion test apparatus 3100 of this embodiment includes a first drive unit 3110, a second drive unit 3120, and a control unit C3 that controls the operation of the torsion test apparatus 3100 in an integrated manner.

[0136] First, the structure of the first driving unit 3110 will be described. FIG. 27 is a side view of the first driving unit 3110 with a part cut away. The first driving unit 3110 includes a main body 3110a and a base 3110b that supports the main body 3110a at a predetermined height. The main body 3110a includes a servo motor unit 150, a reducer 3113, a case 3114, a spindle 3115, a chuck device 3116, a torque sensor 3117, a slip ring 3119a, and a brush 3119b, and the main body 3110a is assembled on a movable plate 3111 horizontally disposed on the top of the base 3110b. The servo motor unit 150 is the same as that in the first embodiment. The servo motor unit 150 is fixed on the movable plate 3111 with the output shaft (not shown) facing horizontally. Further, the movable plate 3111 of the base 3110b is provided so as to be slidable in the direction of the output axis of the servo motor unit 150 (the left-right direction in FIG. 26).

[0137] An output shaft (not shown) of the servo motor unit 150 is connected to an input shaft (not shown) of the reducer 3113 by a coupling (not shown). An output shaft 3113a of the reducer 3113 is connected to one end of a torque sensor 3117. The other end of the torque sensor 3117 is connected to one end of a spindle 3115. The spindle 3115 is rotatably supported by a bearing 3114a fixed to a frame 3114b of a case 3114. A chuck device 3116 for attaching one end (one of the rotating shafts) of the test piece T1 to the first driving part 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 decelerated by the reducer 113 and then transmitted to one end of the test piece T1 via the torque sensor 3117, the spindle 3115, and the chuck device 3116. In addition, a rotary encoder (not shown) that detects the rotation angle of the spindle 3115 is attached to the spindle 3115.

[0138] 27, the reducer 3113 is fixed to a frame 3114b of a case 3114. The reducer 3113 also includes a gear case and a gear mechanism rotatably supported by the gear case via a bearing (not shown). That is, the case 3114 covers a power transmission shaft from the reducer 3113 to the chuck device 3116, and also functions as a device frame that rotatably supports the power transmission shaft at the positions of the reducer 3113 and the spindle 3115. That is, 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 a bearing. Therefore, the torque sensor 3117 is not subjected to bending moment due to the gear mechanism of the reducer 3113 or the weight of the spindle 3115 (and chuck device 3116), but is subjected to only the test load (torsion load), so that the test load can be detected with high accuracy.

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

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

[0141] In the torsion test apparatus 3100 of this embodiment, the output shaft O and the input shaft I (engine side) of the specimen T1, which is a transmission unit for an FR vehicle, are fixed to the chuck devices 3116 and 3126 of the first drive unit 3110 and the second drive unit 3120, respectively, and are rotated synchronously by the servo motor units 150 and 150, while a difference is provided between the rotational speeds (or rotation phases) of the two chuck devices 3116 and 3126, thereby applying a torsional load to the specimen T1. For example, the chuck device 3126 of the second drive unit 3120 is rotated 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 varies according to a predetermined waveform, thereby applying a periodically varying torque to the specimen T1, which is the transmission unit.

[0142] In this way, the torsion test apparatus 3100 of this embodiment is capable of precisely driving both the input shaft I and the output shaft O of the transmission unit by the servo motor units 150, 150, and therefore, by applying a fluctuating torque to each shaft of the transmission unit while driving the transmission unit to rotate, it is possible to perform testing under conditions close to the actual driving conditions of an automobile.

[0143] When performing a rotational torsion test on a device in which an input shaft I and an output shaft O are connected via gears, such as a transmission unit, the magnitude of the torque applied to the input shaft I and the output shaft O does not necessarily match. Therefore, in order to more accurately grasp 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, since torque sensors are provided on both the first drive unit 3110 and the second drive unit 3120 as described above, 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 side of the transmission unit is rotated at a constant speed, and a torque is applied to the output shaft O side. However, the present invention is not limited to the above example. That is, the output shaft O side of the transmission unit may be rotated at a constant speed, and a variable torque may be applied to the input shaft I side. Alternatively, both the input shaft I side and the output shaft O side of the transmission unit may be rotated at a variable rotation speed. Also, the rotation speed may not be controlled, and only the torque of each shaft may be controlled. Also, the torque and the rotation speed may be changed according to a predetermined waveform. The torque and the rotation speed can be changed according to an arbitrary waveform generated by, for example, a function generator. Also, the torque and the rotation speed of each shaft of the test specimen T1 can be controlled based on the waveform data of the torque and the rotation speed measured in an actual driving test.

[0145] The torsion test apparatus 3100 of this embodiment is capable of adjusting the distance between the chuck devices 3116 and 3126 so as to accommodate transmission units of various dimensions. Specifically, a movable plate driving mechanism (not shown) allows the movable plate 3111 of the first driving unit 3110 to move in the direction of the rotation axis of the chuck device 3116 relative to the base 3110b (left and right direction in FIG. 26). During the rotation torsion test, the movable plate 3111 is firmly fixed to the base 3110b by a locking mechanism (not shown). The second driving unit 3120 also includes a movable plate driving mechanism similar to that of the first driving unit 3110.

[0146] The torsion test apparatus 3100 according to the thirteenth embodiment of the present invention described above is adapted to perform a rotational torsion test on a transmission unit for an FR vehicle, but the present invention is not limited to the configuration of the basic example of the thirteenth embodiment described above, and the present invention also includes apparatuses for performing rotational torsion tests on other power transmission mechanisms. The first, second, and third modified examples of the thirteenth embodiment of the present invention described below are examples of the configuration of a torsion test apparatus suitable for testing a transmission unit for an FF vehicle, a differential gear unit, and a transmission unit for a 4WD vehicle, respectively.

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

[0148] The torsion test apparatus 3200 of this modification includes a first drive section 3210 that drives the input shaft I of the test specimen T2, a second drive section 3220 that drives the left output shaft OL, and a third drive section 3230 that drives the right output shaft OR. The torsion test apparatus 3200 also includes a control unit C3a that controls the overall operation of the apparatus. The structures of the first drive section 3210, the second drive section 3220, and the third drive section 3230 are all the same as those of the first drive section 3110 and the second drive section 3120 according to the basic example of the thirteenth embodiment described above, and therefore a description of the overlapping specific configurations will be omitted.

[0149] When performing a rotational torsion test on the specimen T2 using the torsion test apparatus 3200 of this modified example, for example, the input shaft I is driven at a predetermined rotation 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 that a predetermined torque is applied.

[0150] By controlling the first drive unit 3210, the second drive unit 3220, and the third drive unit 3230 as described above, it is possible to perform testing under conditions close to the actual driving conditions of an automobile by applying a fluctuating torque to each shaft of the transmission unit while rotating the transmission unit.

[0151] In addition, the transmission unit to be tested using the torsion test device 3200 of this modification is a device in which the input shaft I, the left output shaft OL, and the right output shaft OR are connected via gears, etc., and when performing a rotational torsion test, the magnitudes of the torques applied to the input shaft I, the left output shaft OL, and the right output shaft OR do not match. In addition, the torques applied to the left output shaft OL and the right output shaft OR do not necessarily match. Therefore, in order to more accurately grasp the behavior of the test specimen T2 during the torsion test, it is preferable to be able to measure the torques applied to the input shaft I, the left output shaft OL, and the right output shaft OR individually. In this modification, since the first drive unit 3210, the second drive unit 3220, and the third drive unit 3230 are all provided with torque sensors, the torques 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] In addition, 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 have 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 the torque of the left output shaft OL and the torque of the right output shaft OR have different (e.g., opposite phase) waveforms.

[0153] Also, the left output shaft OL and the right output shaft OR may be configured to rotate at a constant speed, and the input shaft I may be driven so that the speed varies at a constant period. Alternatively, the input shaft I, the left output shaft OL, and the right output shaft OR may all be driven so that the rotation speed varies independently.

[0154] (Second modified example of the thirteenth embodiment) Next, a second modified example of the thirteenth embodiment of the present invention will be described. Fig. 19 is a plan view of a torsion test apparatus 3300 according to this modified example. This modified example is an example of the configuration of a torsion test apparatus suitable for a rotational torsion test using a differential gear unit for a FR vehicle as specimen T3. As with the first modified example, specimen T3 has an input shaft I, a left output shaft OL, and a right output shaft OR.

[0155] The torsion test apparatus 3300 of this modification includes a first drive section 3310 that drives the input shaft I of the specimen T3, a second drive section 3320 that drives the left output shaft OL, and a third drive section 3330 that drives the right output shaft OR. The torsion test apparatus 3300 also includes a control unit C3b that controls the overall operation of the apparatus. The structures of the first drive section 3310, the second drive section 3320, and the third drive section 3330 are all the same as the first drive section 3110 and the second drive section 3120 according to the basic example of the thirteenth embodiment, and therefore a description of the overlapping specific configurations will be omitted.

[0156] When performing a rotational torsion test on the specimen T3 using the torsion test apparatus 3300 of this modified example, for example, the input shaft I is driven at a predetermined rotation 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 so as 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 test can be performed under conditions close to actual usage conditions by applying a fluctuating torque to each shaft of the test specimen T3 while rotating each shaft of the test specimen T3.

[0158] Similarly to the transmission unit, the differential gear unit is also a device in which the input shaft I is connected to the left output shaft OL and the right output shaft OR via gears, and when performing a rotational torsion test, 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. In addition, the magnitude of the torque applied to the left output shaft OL and the right output shaft OR does not necessarily match. Therefore, in order to more accurately grasp 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 the first drive unit 3310, the second drive unit 3320, and the third drive unit 3330 are all provided with torque sensors, the torque applied to each of 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] In addition, the second drive unit 3320 and the third drive unit 3330 may be controlled so that the rotation speed of the input shaft I and the rotation speeds of the left output shaft OL and the right output shaft OR draw the same waveform, or the second drive unit 3320 and the third drive unit 3330 may be controlled so that the two draw different waveforms (for example, such that the speed difference with the input shaft I is in opposite phase).

[0160] Also, the left output shaft OL and the right output shaft OR may be configured to rotate at a constant speed, and the input shaft I may be driven so that the speed varies at a constant period. Alternatively, all of the input shaft I, the left output shaft OL, and the right output shaft OR may be configured to be driven so that the rotation speed varies.

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

[0162] The torsion test device 3400 of this modification 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 test device 3400 also includes a control unit C3c that controls the overall operation of the device. 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 the first drive unit 3110 and the second drive unit 3120 of the basic example of the thirteenth embodiment, so that a description of the overlapping specific configurations will be omitted.

[0163] Fourteenth embodiment In the above first to thirteenth embodiments, the two-shaft output servo motor 150A according to the embodiment of the present invention is used in conjunction with a servo motor 150B having one output shaft, but the two-shaft output servo motor 150B can also be used alone, as in the fourteenth embodiment of the present invention described next.

[0164] 31 is a side view of a torsion test apparatus 4000 according to a fourteenth embodiment of the present invention. The torsion test apparatus 4000 is an apparatus that enables a rotational torsion test of two specimens T3a and T3b to be performed simultaneously using only one two-axis output servomotor 150A. The torsion test apparatus 4000 includes a fixed base 4100, a drive section 4200, a first reaction force section 4400A, a second reaction force section 4400B, and a control unit C4.

[0165] 32 is an enlarged view of the drive unit 4200. The drive unit 4200 includes 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 a control unit C4, and the drive is controlled by the control unit C4. The drive transmission units 4200A and 4200B reduce the speed of 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 the rotation to the input shafts of the test pieces T3a and T3b. Since the drive transmission units 4200A and 4200B have the same configuration, the details of the configuration will be described for only one of the drive transmission units 4200A.

[0166] The drive transmission unit 4200A includes a frame 4210, a reducer 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 member)-shaped frame mounted on a fixed base 4100, and includes a bottom plate 4212, which is a flat plate horizontally arranged 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 vertically connected to the bottom plate 4212 and the vertical plate 4214. The bottom plate 4212, the vertical plate 4214, and the rib plate 4216 are mutually connected by welding. The vertical plate 4214 is arranged perpendicular to the first output shaft 150A2a of the two-shaft output servo motor 150A, and has an opening 4214a formed coaxially with the first output shaft 150A2a. A reducer 4220 is inserted and fixed in an opening 4214a of the vertical plate 4214.

[0167] A first bracket 150A3 of the two-shaft output servo motor 150A is attached with bolts to an input side flange plate 4224 of the reducer 4220. The first bracket 150A3 is fixed to the input side flange plate 4224 via a reinforcing plate 4212 not only by the mounting seat surface (the right side surface in FIG. 31) but also by tapped holes 150A3t provided on the underside thereof. This allows the input side flange plate 4224 of the reducer 4220 and the first bracket 150A3 of the two-shaft output servo motor 150A to be connected with high rigidity, enabling high-precision testing.

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

[0169] The reducer 4220 is provided with an oil supply cup 4222, and the internal space of the reducer 4220 is filled with lubricating oil, so that each gear constituting the reducer 4220 is always completely immersed in the lubricating oil. In the torsion test, a reciprocating torsional load in the normal range is applied to the test specimen, so the twist angle of the test specimen is at most several tens of degrees, and the amplitude of the repeated rotation of the input shaft of the reducer is often less than one rotation (360 degrees). By filling the internal space of the reducer 4220 with lubricating oil, the oil film of the gear mechanism constituting the reducer is prevented from running out even in such a usage form, and the heat dissipation effect of the lubricating oil is enhanced, effectively preventing seizure of the tooth surface.

[0170] A pulley 4230 is provided on the outer periphery of the output shaft 4228. A rotary encoder 4250 is disposed on the vertical plate 4214 of the frame 4210 below the reducer 4220. A timing belt 4240 is wound around a pulley 4252 attached to the input shaft of the rotary encoder 4250 and a pulley 4230 attached to the output shaft 4228 of the reducer 4220, and the rotation of the output shaft 4228 of the reducer 4220 is transmitted to the rotary encoder 4250 via the timing belt 4240 and detected. The rotary encoder 4250 is connected to the control unit C4, and a signal indicating the rotation detected by the rotary encoder 4250 is sent to the control unit C4.

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

[0172] The first reaction force section 4400A includes a frame 4410, a torque sensor 4420, a spindle 4440, a bearing section 4460, and a chuck device 4480. The frame 4410 is an angle (L-shaped bar)-shaped frame attached to the fixed base 4100 with a bolt B, and includes a bottom plate section 4412 arranged horizontally on the fixed base 4100, a vertical plate 2414 which is a flat plate standing upright from one end of the upper surface of the bottom plate section 4412 (the left end in FIG. 31), and a pair of rib plates 2416 which are vertically connected to the bottom plate section 4412 and the vertical plate 2414. The bottom plate section 4412, the vertical plate 4214, and the rib plate 4216 are mutually connected by welding. The bearing section 4460 is fixed to the bottom plate section 4412 with a bolt B on the drive section 4200 side of the vertical plate 2414 and the rib plate 2416.

[0173] The fixed base 4100 includes a first reaction force part moving mechanism (not shown) for smoothly moving the first reaction force part 4400A in the direction of the first output shaft 150A2a of the dual-axis output servo motor 150A, and the first reaction force part moving mechanism can be operated in a state where the bolt B for fixing the bottom plate part 4412 to the fixed base 4100 is loosened, thereby making it possible to smoothly move the first reaction force part 4400A in the direction of the first output shaft 150A2a. The fixed base 4100 also includes a second reaction force part moving mechanism (not shown) for smoothly moving the second reaction force part 4400B in the direction of the second output shaft 150A2b of the dual-axis output servo motor 150A.

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

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

[0176] Moreover, the spindle 4440 is rotatably supported near the other end (the end on the chuck device 4480 side) by a bearing portion 4460. Therefore, the torque sensor 4420 and the spindle 4440 are supported at both ends by the vertical plate 2414 and the bearing portion 4460, so that it is possible to prevent a detection error of the torque sensor 4420 from increasing due to a large bending moment being applied to the torque sensor 4420.

[0177] When a rotational torsion test is performed using the torsion test apparatus 4000 having the above configuration, as described above, the input shaft of the specimen T3a is attached to the chuck device 4260 of the drive transmission unit 4200A, and the output shaft of the specimen T3a is attached to the chuck device 4480 of the first reaction force unit 4400A. Similarly, the input shaft of the specimen T3b is attached to the chuck device 4260 of the drive transmission unit 4200B, and the output shaft of the specimen T3b is attached to the chuck device 4480 of the second reaction force unit 4400B. When the two-shaft 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. As a result, the same amount of torsion is applied to the specimens T3a and T3b, i.e., the torsion tests are performed under the same conditions on the specimens T3a and T3b.

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

[0179] Moreover, by providing a linear converter such as a feed screw mechanism instead of the drive transmission parts 4200A and 4200B, a tension-compression test device can be obtained that repeatedly applies a compressive force and a tensile force to two specimens T3a and T3b (or applies a compressive force to one of the specimens T3a and T3b and a tensile force to the other). With this configuration, it becomes possible to simultaneously perform a repeated stretching test on the two specimens T3a and T3b (or a tensile test on the specimen T3a and a compression test on the specimen T3b). In addition, by eliminating the first reaction part 4400A and the second reaction part 4400B, it becomes possible to simultaneously perform a vibration test on the two specimens T3a and T3b.

[0180] Fifteenth embodiment The two-axis output servo motor 150A and the servo motor unit 150 according to the embodiment of the present invention can be used as a drive source for a linear actuator in combination with a linear converter such as a feed screw mechanism. By using such a linear actuator, for example, a vibration test device or a tension / compression test device can be realized.

[0181] Fig. 33 is a top view of a vibration testing apparatus (vibration device) 5000 according to a fifteenth embodiment of the present invention. In the vibration testing apparatus 5000 of this embodiment, a workpiece to be subjected to a vibration test is fixed on a table 5100, and the table 5100 and the workpiece thereon are vibrated in three orthogonal axial directions using first, second, and third actuators 5200, 5300, and 5400. In the following description, the direction in which the first actuator 5200 vibrates the table 5100 (the up-down direction in Fig. 33) is defined as the X-axis direction, the direction in which the second actuator 5300 vibrates the table 5100 (the left-right direction in Fig. 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 (the direction perpendicular to the paper surface in Fig. 33), is defined as the Z-axis direction.

[0182] Fig. 38 is a block diagram of a 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 provided with vibration sensors 5220, 5320, and 5420, respectively. The control unit C5 feedback-controls the first, second, and third actuators 5200, 5300, and 5400 (specifically, servo motor units 150X, 150Y, and 150Z) based on the outputs of these vibration sensors, thereby vibrating the table 5100 and the workpiece mounted thereon with a desired amplitude and frequency (these parameters are usually set as a function of time). The servo motor units 150X, 150Y, and 150Z are the same as the servo motor unit 150 in the first embodiment.

[0183] The first, second and third actuators 5200, 5300 and 5400 are configured such that motors, power transmission members and the like are attached onto base plates 5202, 5302 and 5402, respectively. These base plates 5202, 5302 and 5402 are fixed onto the device base 5002 by bolts (not shown).

[0184] In addition, on the device base 5002, adjusters A are arranged at a plurality of positions close to the base plates 5202, 5302, and 5402. The adjuster A has a female screw portion A1 fixed to the device base 5002 with a bolt AB, and a male screw portion A2 screwed into the female screw portion A1. The male screw portion A2 is a columnar member with a screw thread formed on a cylindrical surface, and the male screw portion A2 can be advanced and retreated relative to the corresponding base plate by engaging the male screw portion A2 with a screw hole formed in the female screw portion A1 and rotating it. One end portion (the side proximal to the corresponding base plate) of the male screw portion A2 is formed in a substantially spherical shape, and the position of the base plate can be finely adjusted by abutting this protruding portion against the side surface of the corresponding base plate. In addition, a hexagonal hole for a hexagonal wrench (not shown) is formed in the other end portion (the side distal to the corresponding base plate) of the male screw portion A2. In addition, once base plates 5202, 5302, 5402 are fixed, nut A3 is attached to male thread portion A2 to prevent male thread portion A2 from loosening due to vibrations that may be transmitted from the base plates to adjuster A during a vibration test. Nut A3 is attached so that one end face thereof abuts female thread portion A1, and from this state, nut A3 is screwed in to push female thread portion A1, applying an axial force to male thread portion A2 and female thread portion A1, and the frictional force generated by this axial force on the threads of male thread portion A2 and female thread portion A1 prevents female thread portion A1 from loosening from male thread portion A2.

[0185] Next, the configuration of the first actuator 5200 will be described. FIG. 34 is a side view of the first actuator 5200 according to an embodiment of the present invention as viewed in the Y-axis direction (from the right to the left in FIG. 33). This side view is partially cut away to show the internal structure. FIG. 35 is a top view of the first actuator 5200 with a portion cut away to show the internal structure. In the following description, the direction along the X-axis from the first actuator 5200 to the table 5100 is defined as the "X-axis positive direction," and the direction along the X-axis from the table 5100 to the first actuator is defined as the "X-axis negative direction."

[0186] 34, a frame 5222 consisting of a plurality of beams 5222a welded together and a top plate 5222b is fixed by welding onto the base plate 5202. In addition, a bottom plate 5242 of a support mechanism 5240 for supporting a drive mechanism 5210 for vibrating the table 5100 (FIG. 33) and a connecting mechanism 5230 for transmitting the vibration motion of the drive mechanism 5210 to the table 5100 is fixed onto 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 portion 5216, a ball screw 5218, and a ball nut 5219. The coupling 5260 couples the drive shaft 152X of the servo motor unit 150X to the ball screw 5218. The bearing portion 5216 is supported by a bearing support plate 5244 that is fixed by welding perpendicularly to a bottom plate 5242 of the support mechanism 5240, and rotatably supports the ball screw 5218. The ball nut 5219 is engaged 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 advances and retreats 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 connecting mechanism 5230, thereby driving the table 5100 in the X-axis direction. Then, by controlling the servo motor unit 150X so as to switch the rotation direction of the servo motor unit 150X in a short period, it is possible to vibrate the table 5100 in the X-axis direction with a desired amplitude and period.

[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 surface (the surface on the X-axis negative direction side) of the motor support plate 5246 so that the drive shaft 152X is perpendicular to the motor support plate 5246. An opening 5246a is provided in the motor support plate 5246, and the drive shaft 152X of the servo motor unit 150X passes through this opening 5246a and is connected to the ball screw 5218 on the other surface side of the motor support plate 5246.

[0189] Since the servo motor unit 150X is supported by the motor support plate 5246 in a cantilever manner, a large bending stress is applied to the motor support plate 5246, particularly at the welded portion with the bottom plate 5242. In order to relieve this bending stress, a rib 5248 is provided between the bottom plate 5242 and the motor support plate 5246.

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

[0191] Next, a description will be given of the configuration of the connecting portion 5230. The connecting portion 5230 has a nut guide 5232, a pair of Y-axis rails 5234, a pair of Z-axis rails 5235, an intermediate stage 5231, a pair of X-axis rails 5237, a pair of X-axis runner blocks 5233, and a runner block mounting member 5238.

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

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

[0194] The pair of X-axis rails 5237 are rails that both extend in the X-axis direction, and are fixed to the bottom plate 5242 of the support mechanism 5240 in a line in the Y-axis direction. The X-axis runner block 5233 engages with each of the X-axis rails 5237 and is slidable along the X-axis rails 5237. The runner block mounting member 5238 is a member fixed to the bottom surface of the nut guide 5232 so as to protrude toward both sides in the Y-axis direction, and the X-axis runner block 5233 is fixed to the bottom of the runner block mounting member 5238. In this way, the nut guide 5232 is guided by the X-axis rails 5237 via the runner block mounting member 5238 and the X-axis runner block 5233, and is thereby movable only in the X-axis direction.

[0195] In this way, since the movement direction of the nut guide 5232 is limited to only the X-axis direction, when the servo motor unit 150X is driven to rotate the ball screw 5218, the nut guide 5232 and the table 5100 engaged with this nut guide 5232 advance and retreat in the X-axis direction.

[0196] A position detection means 5250 is disposed on one side surface (the near side in FIG. 34, the right side in FIG. 35) 5238a on the Y-axis direction side of the runner block mounting member 5238. The position detection means 5250 has three proximity sensors 5251 arranged at regular intervals in the X-axis direction, a detection plate 5252 provided on the side surface 5238a of the runner block mounting member 5238, and a sensor support plate 5253 supporting the proximity sensor 5251. The proximity sensor 5251 is an element capable of detecting whether or not any object is in proximity (for example, within 1 millimeter) in front of each proximity sensor. Since the side surface 5238a of the runner block mounting member 5238 and the proximity sensor 5251 are sufficiently separated, the proximity sensor 5251 can detect whether or not the detection plate 5252 is in front of each proximity sensor 5251. The control unit C5 of the vibration testing device 5000 can feedback-control the servo motor unit 150X using the detection result of the proximity sensor 5251, for example (FIG. 38).

[0197] In addition, on the bottom plate 5242 of the support mechanism 5240, there are provided restriction blocks 5236 arranged to sandwich the X-axis runner block 5233 from both sides in the X-axis direction. The restriction blocks 5236 are for limiting the movement range of the nut guide 5232. That is, when the servo motor unit 150X is driven to continue moving the nut guide 5232 in the X-axis positive direction, the restriction block 5236 arranged on the X-axis positive direction side and the runner block mounting member 5238 eventually come into contact with each other, and the nut guide 5232 cannot move any further in the X-axis positive direction. The same is true when the nut guide 5232 continues to move in the X-axis negative direction, and the restriction block 5236 arranged on the X-axis negative direction side and the runner block mounting member 5238 come into contact with each other, and the nut guide 5232 cannot move any further in the X-axis negative 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-axis and the Y-axis are interchanged), and therefore a detailed description of the second actuator 5300 will be omitted.

[0199] Next, the configuration of the third actuator 5400 according to the embodiment of the present invention will be described. FIG. 36 is a side view of the table 5100 and the third actuator 5400 as viewed from the X-axis direction (from the bottom to the top in FIG. 16). This side view is also partially cut away to show the internal structure. FIG. 37 is a side view of the table 5100 and the third actuator 5400 according to the embodiment of the present invention as viewed from the Y-axis direction (from the left to the right in FIG. 33). FIG. 37 is also partially cut away to show the internal structure. In the following description, the direction along the Y-axis from the second actuator 5300 to the table 5100 is defined as the Y-axis positive direction, and the direction along the Y-axis from the table 5100 to the second actuator 5300 is defined as the Y-axis negative direction.

[0200] As shown in Fig. 36 and Fig. 37, a frame 5422 is provided on a base plate 5402, which is composed of a plurality of beams 5422a extending in the vertical direction and a top plate 5422b arranged to cover the plurality of 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 a support mechanism 5440 is fixed to the top plate 5422b of the frame 5422 via a bolt (not shown). This bearing support plate 5442 is a member for supporting a drive mechanism 5410 for vibrating the table 5100 (Fig. 33) in the vertical direction and a connecting mechanism 5430 for transmitting the vibration motion by the drive mechanism 5410 to the table.

[0201] The drive mechanism 5410 includes a servo motor unit 150Z, a coupling 5460, a bearing portion 5416, a ball screw 5418, and a ball nut 5419. The coupling 5460 couples the drive shaft 152Z of the servo motor unit 150Z to the ball screw 5418. The bearing portion 5416 is fixed to the bearing support plate 5442 described above, and rotatably supports the ball screw 5418. The ball nut 5419 is engaged 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 advances and retreats in its axial direction (i.e., the Z-axis direction). The motion of the ball nut 5419 is transmitted to the table 5100 via the connecting mechanism 5430, and the table 5100 is driven in the Z-axis direction. By controlling the servo motor unit 150Z so as to switch the rotation direction of the servo motor unit 150Z in a short period, it is possible to vibrate the table 5100 in the Z-axis direction (up and down direction) with a desired amplitude and period.

[0202] A motor support plate 5446 extending in the horizontal direction (XY plane) is fixed to the lower surface of a 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. An opening 446a is provided in the motor support plate 5446, and a drive shaft 152Z of the servo motor unit 150Z passes through this opening 446a and is connected to a ball screw 5418 on the upper surface side of the motor support plate 5446.

[0203] In this embodiment, since the axial dimension (vertical direction, Z-axis direction) of the servo motor unit 150Z is larger than the height of the frame 5422, most of the servo motor unit 150Z is disposed at a position lower than the base plate 5402. For this reason, the device base 5002 is provided with a hollow portion 5002a for accommodating the servo motor unit 150Z. Also, the base plate 5402 is provided with an opening 5402a for passing the servo motor unit 150Z.

[0204] The bearing portion 5416 is provided so as to penetrate the bearing support plate 5442. The structure of the bearing portion 5416 is similar to that of the bearing portion 5216 in the first actuator 5200 (FIGS. 34 and 35), and therefore detailed description thereof will be omitted.

[0205] Next, a description will be given of the configuration of the connecting portion 5430. The connecting portion 5430 has a movable frame 5432, a pair of X-axis rails 5434, a pair of Y-axis rails 5435, a plurality of intermediate stages 5431, two pairs of Z-axis rails 5437, and two pairs of Z-axis runner blocks 5433.

[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 in the X-axis direction of the top plate 5432b. The pair of Y-axis rails 5435 are rails that both extend in the Y-axis direction and are fixed to the upper surface of the top plate 5432b of the movable frame 5432 side by side in the X-axis direction. The pair of X-axis rails 5434 are rails that both extend in the X-axis direction and are fixed to the lower surface of the table 5100 side by side in the Y-axis direction. The intermediate stage 5431 is a block in which an X-axis runner block 5431a that engages with the X-axis rail 5434 is provided at the top and a Y-axis runner block 5431b that engages with each of the Y-axis rails 5435 is provided at the bottom, and is configured to be slidable with respect to both the X-axis rail 5434 and the Y-axis rail 435. The intermediate stages 5431 are provided at each position where the X-axis rails 5434 and the Y-axis rails 5435 intersect. Since two X-axis rails 5434 and two Y-axis rails 5435 are provided, the X-axis rails 5434 and the Y-axis rails 5435 intersect at four positions. Therefore, in this embodiment, four intermediate stages 5431 are used.

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

[0208] In addition, in this embodiment, since the movable frame 5432 supports the table 5100 and workpiece, which are relatively heavy, the distance between the X-axis rail 5434 and the Y-axis rail 5435 is wider than the distance between the Y-axis rail 5234 and the Z-axis rail 5235 of the first actuator 5200. For this reason, if the table 5100 and the movable frame 5432 are connected by only one intermediate stage as in the first actuator 5200, the intermediate stage becomes large and the load applied to the movable frame 5432 increases. For this reason, in this embodiment, a small intermediate stage 5431 is arranged at each intersection of the X-axis rail 5434 and the Y-axis rail 5435, and the magnitude of the load applied to the movable frame 5432 is kept to a necessary minimum.

[0209] The two pairs of Z-axis rails 5437 are rails extending in the Z-axis direction, and are fixed in pairs to each of the side walls 5432c of the movable frame 5432 in the Y-axis direction. The Z-axis runner block 5433 engages with each of the Z-axis rails 5437 and is slidable along the Z-axis rails 5437. The Z-axis runner block 5433 is fixed to the upper surface of the top plate 5422b of the frame 5422 via a runner block mounting member 5438. The runner block mounting member 5438 has a side plate 5438a arranged approximately parallel to the side wall 5432c of the movable frame 5432 and a bottom plate 5438b fixed to the lower end of the side plate 5438a, and has an L-shaped cross section as a whole. In this embodiment, when a workpiece with a particularly high center of gravity and a large weight is fixed on the table 5100, a large moment around the X-axis and / or the Y-axis is easily applied to the movable frame 5432. Therefore, the runner block mounting member 5438 is reinforced by ribs so as to withstand this rotation moment. Specifically, a pair of first ribs 5438c are provided at the corners formed by the side plates 5438a and the bottom plate 5438b at both ends in the Y-axis direction of the runner block mounting member 5438, and further, a second rib 5438d is provided between the pair of first ribs 5438c.

[0210] In this manner, 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 any direction other than the vertical direction is restricted. Since the movement direction of the movable frame 5432 is restricted only to the vertical direction, when the servo motor unit 150Z is driven to rotate the ball screw 5418, the movable frame 5432 and the table 5100 engaged with this movable frame 5432 advance and retreat in the vertical direction.

[0211] Moreover, the third actuator 5400 is also provided with a position detection means (not shown) similar to the position detection means 5250 (FIGS. 34 and 35) of the first actuator 5200. The control unit C5 of the vibration testing apparatus 5000 can control the height of the movable frame 5432 to be within a predetermined range based on the detection result of this position detection means (FIG. 38).

[0212] As described above, in this embodiment, two pairs of rails and an intermediate stage configured to be slidable relative to the rails are provided between each actuator and the table 5100, whose drive axes are perpendicular to each other. This allows the table 5100 to slide in any direction on a plane perpendicular to the drive direction of the actuator. Therefore, even if the table 5100 is displaced by an actuator, the load or moment caused by this displacement is not applied to the other actuators, and the state in which the other actuators and the table 5100 are engaged via the intermediate stage is maintained. In other words, even if the table is displaced to an arbitrary position, the state in which each actuator can displace the table is maintained. Therefore, in this embodiment, the three actuators 5200, 5300, and 5400 can be driven simultaneously to vibrate the table 5100 and the work fixed thereon in three axial directions.

[0213] In this embodiment, as described above, a connection portion equipped with a guide mechanism combining a rail and a runner block is provided between the actuators 5200, 5300, 5400 and the table 5100. A similar guide mechanism is also provided in the actuators 5200, 5300, 5400, and this guide mechanism is used to guide the nut of the ball screw mechanism of each actuator.

[0214] In addition, in each of the above embodiments, an ultra-low inertia servo motor is used in the torque generating device, but the configuration of the present invention is not limited to this. The present invention also includes a configuration using another type of electric motor (e.g., an inverter motor) that has a small moment of inertia of the rotor and can be driven at high acceleration or high jerk. In this case, as in each of the above embodiments, a configuration can be adopted in which an encoder is provided in the electric motor and feedback control is performed based on the rotation state (e.g., rotation speed and angular position) of the output shaft of the electric motor detected by the encoder.

[0215] Although the above embodiment is an example of application of the present invention to a durability test device for a power transmission device for an automobile, the present invention is not limited thereto and can be used for various applications in the general industry. For example, the present invention can be used to evaluate the mechanical properties and durability of two-wheeled vehicles, agricultural machinery, construction machinery, railroad cars, ships, aircraft, power generation systems, water supply and drainage systems, or various components that constitute these systems.

[0216] The above is a description of the present embodiment, but the present invention is not limited to the above configuration, and various modifications are possible within the scope of the technical concept of the present invention. For example, in each of the above embodiments, a servo motor unit 150 (or a torque applying servo motor unit 132) is used in which one servo motor 150B (having one output shaft) and one two-shaft output servo motor 150A are connected in two stages, but a configuration may be used in which a servo motor unit is used in which one servo motor 150B and multiple two-shaft output servo motors 150A are connected in three or more stages.

[0217] <Addendum> In order to further expand the range of applications of servo motor type testing equipment, there is a demand for even higher output while maintaining the high acceleration characteristics of ultra-low inertia servo motors.

[0218] In addition, 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 specimens simultaneously using a single servo motor.

[0219] However, simply increasing the output of a servo motor requires increasing the strength of each part of the servo motor, which increases the size and weight by more than the increase in output. This also increases the output ratio of the moment of inertia of the servo motor (the ratio of the moment of inertia to the output of the servo motor), which causes problems such as a decrease in acceleration characteristics (including jerk) and a decrease in the frequency range of the variable load that can be output.

[0220] In addition, because conventional servo motors only have one output shaft, in order to enable simultaneous testing of multiple specimens, it was necessary to install a gear mechanism to distribute the power, which resulted in problems such as increased frictional resistance and larger testing equipment.

[0221] According to one embodiment of the present invention, there is provided a two-shaft output servo motor comprising a cylindrical main body frame, a substantially flat first bracket attached to one axial end of the main body frame, a substantially flat second bracket attached to the other axial end of the main body frame, and a drive shaft passing through a hollow portion of the main body frame, penetrating the first bracket and the second bracket, and supported for free rotation by bearings provided on the first bracket and the second bracket, one end of the drive shaft protruding to the outside from the first bracket as a first output shaft that outputs driving force to the outside, and the other end protruding to the outside from the second bracket as a second output shaft.

[0222] The first bracket and the second bracket may be configured to have a first mounting surface on the opposite side to the surfaces facing each other, the first mounting surface being provided with a tapped hole for mounting a two-axis output servomotor.

[0223] The first bracket and the second bracket may be configured to have a second mounting surface perpendicular to the first mounting surface, the second mounting surface being provided with tapped holes for mounting a dual-axis output servomotor.

[0224] At least one of the first bracket and the second bracket may be provided with a rotary encoder for detecting the rotational position of the drive shaft.

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

[0226] The above servo motor unit may include the above two-axis output servo motor, and a rotary encoder for detecting the rotational position of the drive shaft may be attached to either the load side bracket or the anti-load side bracket, 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 a signal output by the rotary encoder.

[0227] The servo motor unit may include the above-mentioned 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 a signal output from one of the rotary encoders.

[0228] According to one embodiment of the present invention, there is provided a rotary torsion testing device 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 supports the load application unit rotatably about the rotation axis; a rotary drive unit that rotates and drives the first drive shaft and the load application unit in the same phase; and a torque sensor that detects the torsional load, wherein the rotary drive unit rotates the workpiece via the first drive shaft and the second drive shaft, and the load application unit applies a phase difference to the rotations of the first drive shaft and the second drive shaft, thereby applying a load to the workpiece; the load application unit comprises a frame having a cylindrical shaft portion into which the first drive shaft is inserted, the frame being supported at the shaft portion by the first bearing and supporting the first drive shaft; the torque sensor is attached to a portion inserted into the shaft portion of the first drive shaft and is configured to detect the torsional load of the portion; and the load application unit comprises the above-mentioned servo motor unit.

[0229] The rotary torsion test apparatus may include a drive power supply unit arranged outside the load applying unit for supplying drive power to a servo motor unit, a drive power transmission line for transmitting drive power from the drive power supply unit to the servo motor unit, a torque signal processing unit arranged outside the load applying unit for processing a torque signal output by a torque sensor, and a torque signal transmission line for transmitting a torque signal from the torque sensor to the torque signal processing unit, wherein the drive power transmission line includes an external drive power transmission line arranged outside the load applying unit, an internal drive power transmission line arranged inside the load applying unit and rotating together with the load applying unit, and a first slip ring unit connecting the external drive power transmission line and the internal drive power transmission line, and the torque signal transmission line includes an external torque signal transmission line arranged outside the load applying unit, an internal torque signal transmission line wired inside the load applying unit and rotating together with the load applying unit, and a second slip ring unit connecting the external torque signal transmission line and the internal torque signal transmission line, and the second slip ring unit is arranged away from the first slip ring unit.

[0230] The rotational drive unit may include a second motor and a drive force transmission unit that transmits the drive force of the second motor to the load applying unit and the second drive shaft to rotate them in phase, and the drive force transmission unit may include a first drive force transmission unit that transmits the drive force of the second motor to the second drive shaft, and a second drive force transmission unit that transmits the drive force of the second motor to the load applying unit.

[0231] The first driving force transmission unit and the second driving force transmission unit each include an endless belt mechanism, the first driving force transmission unit includes a third driving shaft driven by a second motor arranged parallel to the rotation axis, a first driving pulley fixed coaxially to the third driving shaft, a first driven pulley fixed coaxially to the load applying unit, and a first endless belt stretched between the first driving pulley and the first driven pulley, and the second driving force transmission unit includes a fourth driving shaft coaxially connected to the third driving shaft, a second driving pulley fixed to the fourth driving shaft, a second driven pulley fixed to the first driving shaft, and a second endless belt stretched between the second driving pulley and the second driven pulley.

[0232] According to one embodiment of the present invention, there is provided a torsion test apparatus that applies torque to an input / output shaft of a specimen, which is a power transmission device, and includes a first drive unit connected to the input shaft of the specimen and a second drive unit connected to the output shaft of the specimen, the first drive unit and the second drive unit including the above-mentioned servo motor unit, a reducer that reduces the rotation of the drive shaft of the servo motor unit, a chuck to which the input shaft or output shaft of the specimen is attached and that transmits the output of the reducer to the input shaft or output shaft of the specimen, a torque sensor that transmits the output of the reducer to the chuck and detects the torque output by the reducer, and a tachometer that detects the rotation speed of the chuck.

[0233] The reducer may include a spindle that connects the torque sensor and the chuck, and a bearing portion that supports the spindle for free rotation, and the reducer may include a gear case, a bearing, and a gear mechanism supported by the gear case via the bearing, and the load of the power transmission shaft including the gear mechanism of the reducer 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 reducer.

[0234] According to one embodiment of the present invention, there is provided a torsion test apparatus for simultaneously testing a first specimen and a second specimen, the torsion test apparatus comprising the above-mentioned two-axis output servomotor, a first drive transmission unit for transmitting the rotation of the first output shaft to one end of the first specimen, a first reaction unit for fixing the other end of the first specimen, a second drive transmission unit for transmitting the rotation of the second output shaft to one end of the second specimen, and a second reaction unit for fixing the other end of the second specimen, the first drive transmission unit and the second drive transmission unit comprising a chuck device for mounting one end of the first specimen or the second specimen, the first reaction unit and the second reaction unit comprising a chuck device for mounting the other end of the first specimen or the second specimen, and a torque sensor for detecting torque applied to the first specimen or the second specimen.

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

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

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

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

[0239] According to one embodiment of the present invention, there is provided a vibration device 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; first connecting means for connecting the table to the first actuator so that the table can slide in the second direction; and second connecting means for connecting the table to the second actuator so that the table can slide in the first direction, wherein the first actuator and the second 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 direction or the second direction.

[0240] According to one embodiment of the present invention, there is provided a vibration device 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 direction and the second direction; a first connecting means for connecting the table to the first actuator so as to be slidable in the second direction and the third direction; a second connecting means for connecting the table to the second actuator so as to be slidable in the first direction and the third direction; and a third connecting means for connecting the table to the third actuator so as to be slidable in the first direction and the second direction, 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 direction, the second direction or the third direction.

[0241] According to one embodiment of the present invention, there is provided a torsion testing device comprising: a first servo motor, a cylindrical casing, a second servo motor fixed within the casing, a torque imparting unit having a reducer with an input shaft to which a frame fixed within the casing and an output shaft of the servo motor are connected, and an output shaft that reduces the rotation of the input shaft and outputs it and protrudes from the casing, a first shaft to which a test specimen is attached and one end of which is connected to the output shaft of the reducer, a second shaft of which one end is connected to the output shaft of the motor, a first gearbox having a connection part to which the output shaft of the reducer and a casing of the torque imparting unit are connected and transmitting the rotational motion of the output shaft and the casing via gears, and a second gearbox having a connection part to which the other end of the first shaft and the other end of the second shaft are connected and transmitting the rotational motion of the first shaft and the second shaft via gears.

[0242] According to the present invention, power is circulated via the first gear box and the second gear box. This reduces power loss compared to the conventional configuration in which power is circulated by a belt mechanism, thereby realizing a torsion testing device with lower running costs.

[0243] According to one embodiment of the present invention, there is provided a power simulator comprising an output shaft, a control unit which controls the rotation of the output shaft so as to generate a simulated power which simulates a predetermined power, a rotatably supported load applying unit which applies a torque instructed by the control unit to the output shaft, and a rotation drive unit which rotates and drives the load applying unit at a rotation speed instructed by the control unit, wherein the load applying unit comprises a servo motor whose rotation 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 with high frequency components even at high rotation speeds.

[0245] By making both ends of the drive shaft the first output shaft and the second output shaft, respectively, it becomes possible to distribute the output without adding a power distribution means such as a gear mechanism, and it is possible to prevent an increase in frictional resistance and an increase in the size of the test device that would accompany the addition of a power distribution means. In addition, this configuration makes it possible to combine the outputs by connecting one of the first output shaft and the second output shaft to the output shaft of another servo motor, and it is possible to achieve high output while suppressing an increase in the size of the servo motor and a decrease in acceleration characteristics due to an increase in the moment of inertia that accompanies the increase.

Claims

1. A casing; A bearing portion that rotatably supports the casing; an electric motor attached to the casing; a reducer that reduces the rotation speed of the electric motor; Equipped with The electric motor has a controllable driving amount, The casing comprises: a body portion to which the electric motor is attached; a shaft portion rotatably supported by the bearing portion, The actuator is configured to be connectable to an external drive means, The reduction gear is Equipped with a mounting flange, The mounting flange is fixed to the casing by being sandwiched between the body portion and the shaft portion and tightened, The rotation imparted to the casing by the external driving means is added to the rotation generated by the motor and reduced by the reducer, Load application section.

2. a shaft that is rotated by the electric motor; A bearing is provided on the inner periphery of the cylindrical shaft portion to rotatably support the shaft passing through the hollow portion of the shaft portion. The load-applying portion according to claim 1 .

3. The body portion is cylindrical, The electric motor is disposed in the hollow portion of the body. The load applying portion according to claim 1 or 2.

4. The shaft of the motor is arranged concentrically with the rotation axis of the casing. The load applying portion according to any one of claims 1 to 3.

5. the electric motor comprises a motor case; The motor case is fixed to the casing via a plurality of fixing rods. The load applying portion according to any one of claims 1 to 4.

6. the motor case includes a bracket provided with a second bearing that rotatably supports a shaft of the electric motor, One end of the fixed rod is fixed to the bracket. The load applying portion according to claim 5 .

7. The other end of the fixed rod is fixed to the body portion. The load applying portion according to claim 6 .

8. a power supply unit disposed outside the casing and supplying power to the electric motor; a power transmission line that transmits power from the power supply unit to the electric motor; Equipped with The power transmission path is An external power transmission path disposed outside the casing; an internal power transmission path disposed within the casing and rotatable with the casing; A slip ring portion that connects the external power transmission path and the internal power transmission path is provided. The load applying portion according to any one of claims 1 to 7.

9. A load applying portion according to any one of claims 1 to 8, Mechanical testing equipment.

10. The load applying portion according to any one of claims 1 to 8, a first workpiece mounting portion to which one end of the specimen is attached; a second workpiece mounting portion to which the other end of the specimen is attached; and Equipped with Mechanical testing equipment.

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