JP7389422B2 - Loading section and mechanical testing equipment - Google Patents

Description

The present invention relates to a load applying section and a mechanical testing device .

By adopting an ultra-low inertia servo motor that has significantly reduced inertia compared to conventional servo motors, the present inventors have developed a servo motor that can apply repetitive loads at high frequencies of several tens to hundreds of Hz. We have put into practical use various types of fatigue test devices and vibration test devices (for example, Patent Document 1).

The above-mentioned servo motor type test equipment has many serious problems that conventional hydraulic test equipment had (for example, the need to install large-scale hydraulic supply equipment such as oil tanks and hydraulic piping, and the need to regularly operate a large amount of The scope of application is rapidly expanding as it solves problems such as the need to replace hydraulic oil and contamination of the working environment and soil due to leakage of hydraulic oil.

International Publication No. 2008/133187

An object of the present invention is to provide a load application unit and a mechanical testing device that can independently and highly accurately control each of the rotation speed and torque .

According to one aspect of the present invention, the invention includes a rotatably supported casing, an electric motor attached to the casing, and a connecting shaft rotationally driven by the electric motor, and the electric motor has a rated output of 10 kW or more, The moment of inertia of the rotating part is 10 ^-2 kg・m ² The following load applying section is provided.

The above-mentioned load application part includes a bearing part that rotatably supports the casing, the casing has a cylindrical shaft part rotatably supported by the bearing part, and the casing has a cylindrical shaft part rotatably supported by the bearing part. A configuration may also be provided in which a bearing rotatably supports the connecting shaft passed through the hollow portion.

In the above-described load applying section, the casing may be cylindrical, and the electric motor may be disposed within the hollow part of the casing.

In the load applying section described above, the shaft of the electric motor may be arranged concentrically with the rotation shaft of the casing.

In the load applying section, the electric motor may include a motor case, and the motor case may be fixed to the casing via a plurality of fixing rods.
In the load applying section, the motor case may include a bracket provided with a second bearing that rotatably supports the shaft of the electric motor, and one end of the fixed rod may be fixed to the bracket.

In the above-mentioned load applying section, the casing may include a cylindrical body that houses the electric motor, and the other end of the fixed rod may be fixed to the body.

The above-mentioned load application part is provided with a reducer that decelerates the rotation of the electric motor, the reducer is provided with a mounting flange, and is fixed to the casing by sandwiching and tightening the mounting flange between the body and the shaft. You can also use it as

The above-mentioned load application section includes a power supply section that is arranged outside the casing and supplies power to the electric motor, and a power transmission path that transmits power from the power supply section to the electric motor, and the power transmission path is arranged outside the casing. The device includes an external power transmission path disposed outside, an internal power transmission path arranged inside the casing and rotatable together with the casing, and a slip ring portion connecting the external power transmission path and the internal power transmission path. It may also be a configuration.

According to one aspect of the present invention, a mechanical testing device is provided that includes the above-described load applying section.

According to another aspect of the present invention, the above-described load applying part, a first workpiece attachment part to which one end of the specimen is attached, and a second workpiece attachment part to which the other end of the specimen is attached. ,
A mechanical testing device is provided.

According to one aspect of the present invention, it becomes possible to control each of the rotation speed and torque independently and with high precision .

1 is a side view of a two-axis output servo motor according to an embodiment of the present invention. FIG. 2 is a side view of a servo motor unit according to an embodiment of the present invention. It is a longitudinal cross-sectional view of a modification of the servo motor unit according to the embodiment of the present invention. FIG. 1 is a side view of a rotating torsion testing device according to a first embodiment of the present invention. FIG. 2 is a longitudinal cross-sectional view of the vicinity of the load applying section of the rotary torsion testing device according to the first embodiment of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is a block diagram showing a schematic configuration of a control system of a rotary torsion testing device according to a first embodiment of the present invention. FIG. 3 is an external view of a power simulator according to a modification of the first embodiment of the present invention. FIG. 3 is an external view of a power simulator according to a modification of the first embodiment of the present invention. FIG. 7 is a side view of a test device including a power simulator according to a modification of the first embodiment of the present invention. FIG. 3 is a partially enlarged view of a test device including a power simulator according to a modification of the first embodiment of the present invention. FIG. 3 is a plan view of a rotational torsion testing device according to a second embodiment of the present invention. FIG. 3 is a side view of a rotational torsion testing device according to a second embodiment of the present invention. FIG. 7 is a longitudinal cross-sectional view of the vicinity of a load application portion of a rotary torsion testing device according to a second embodiment of the present invention. It is a top view and a side view of the torsion test device based on 3rd Embodiment of this invention. FIG. 7 is a side sectional view of a torque applying section of a torsion testing device according to a third embodiment of the present invention. It is a top view of the torsion test device based on 4th Embodiment of this invention. It is a top view of the torsion test device based on 5th Embodiment of this invention. It is a top view of the torsion test device based on 6th Embodiment of this invention. FIG. 7 is an external view of a rotational torsion testing device according to a seventh embodiment of the present invention. It is an external view of the rotary torsion test device based on 8th Embodiment of this invention. It is a top view of the tire wear test apparatus based on 9th Embodiment of this invention. It is an external view of the tire testing device concerning a 10th embodiment of the present invention. It is an external view of the tire testing device concerning a 10th embodiment of the present invention. It is an external view of the power absorption type durability test device for FR transmissions concerning an 11th embodiment of the present invention. It is an external view of the power absorption type durability test device for FF transmissions concerning a 12th embodiment of the present invention. It is a side view of the torsion test device concerning a 13th embodiment of the present invention. It is a side view of the 1st drive part of a 13th embodiment of the present invention. It is a top view of the torsion test device based on the 1st modification of the 13th embodiment of the present invention. It is a top view of the torsion test device concerning the 2nd modification of a 13th embodiment of the present invention. It is a top view of the torsion test device concerning the 3rd modification of the 13th embodiment of the present invention. It is a side view of the torsion test device based on a 14th embodiment of the present invention. It is an enlarged view of the drive part of a 14th embodiment of the present invention. It is a top view of the vibration test device concerning a 15th embodiment of the present invention. It is a side view of the 1st actuator concerning a 15th embodiment of the present invention seen from the Y-axis direction. It is a top view of the 1st actuator concerning a 15th embodiment of the present invention. It is a side view of a table and a third actuator of a 15th embodiment of the present invention viewed from the X-axis direction. It is a side view of the table and the 3rd actuator of a 15th embodiment of the present invention seen from the Y-axis direction. It is a block diagram of the control system in the vibration test device concerning a 15th embodiment of the present invention.

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

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

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

One end portion 150A2a (right end portion in FIG. 1) of the drive shaft 150A2 passes through the first bracket 150A3, projects outward from the motor case, and serves as an output shaft 150A2a. Further, the other end portion 150A2b of the drive shaft 150A2 passes through the second bracket 150A4, projects outward from the motor case, and serves as a second output shaft 150A2b. The second bracket 150A4 has a built-in rotary encoder (not shown) that detects the rotation of the other end 150A2b of the drive shaft 150A2.

Furthermore, 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, a fixing tapped hole extending parallel to the drive shaft was provided only on the mounting seat surface (right side in FIG. 1) of the bracket on the load side (the side from which the output shaft protrudes). For applications other than precision machinery testing, fixing using the tapped holes provided on the mounting surface of the load-side bracket is sufficient, but it is especially important for precision machinery testing equipment that applies dynamic loads at high frequencies of several tens of Hz (for example, 20 Hz) or higher. For example, when using a high-output servo motor with a rated output of about 10 kW or more in a fatigue testing device or vibration testing device, it is impossible to fix the servo motor in a direction perpendicular to the drive shaft by simply fixing it on the mounting surface of the bracket. could not be completely fixed, and vibrations with minute amplitudes of, for example, several micrometers to several tens of micrometers were generated, giving a non-negligible error to the test results.

As a result of numerous vibration analyzes and experiments, the inventors found that by adding two fixing tap holes extending perpendicular to the drive shaft on the bottom surface of each bracket, vibration noise becomes noticeable (for example, one (order of magnitude) was found to be improved. In addition to the mounting surface of the load side bracket, tap holes are provided on the bottom surface of each bracket, and by using these tap holes to secure the servo motor with bolts, vibration noise is reduced and higher precision machines can be achieved. Testing becomes possible.

Further, since the servo motor 150A has a high rated output of 37 kW and generates a large amount of heat during operation, the servo motor 150A is configured to radiate the heat generated inside to the outside by water cooling. Two tube joints 150A6 are provided at the top of the main body frame 150A1 to which external piping for supplying and discharging cooling water is connected.

In this embodiment, a servo motor unit 150 is used in which the above-described two-axis 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 invention. Servo motor unit 150 has one drive shaft 152.

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) will be referred to as the load side, and the opposite side will be referred to as the anti-load side. The two-axis output servo motor 150A and servo motor 150B each generate a maximum torque of 350 N・m, and have a rated output of 37 kW, with the moment of inertia of the rotating part suppressed to 10 ⁻² (kg・m ² ) or less. It is a high output ultra-low inertia servo motor.

The servo motor 150B includes a main body frame 150B1, a drive shaft 150B2, a load side bracket 150B3, an anti-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-axis output servo motor 150A. Two tube joints 150B6 to which piping is connected are provided. The anti-load side bracket 150B4 has approximately the same configuration as the second bracket 150A4 of the two-axis output servo motor 150A, but it does not have a built-in rotary encoder, and as described later, the rotary encoder 150B5 is attached to the anti-load side bracket 150B4. It is attached externally. Furthermore, a pair of tapped holes 150B3t and 150B4t are provided on the lower surfaces of the load side bracket 150B3 and the anti-load side bracket 150B4, respectively.

One end portion 150B2a on the load side of the drive shaft 150B2 passes through the load side bracket 150B3, projects outward from the motor case, and serves as an 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 surface (left side in FIG. 2) of the anti-load side bracket 150B4, and the other end 150B2b of the drive shaft 150B2 is It passes through the side bracket 150B4 and is housed within the rotary encoder.

As shown in FIG. 2, the output shaft 152B2a of the servo motor 150B and the second output shaft 150A2b of the two-axis output servo motor 150A are connected by a coupling 150C. Further, the load-side bracket 150B3 of the servo motor 150B and the second bracket 150A4 of the two-axis output servo motor 150A are connected to each other at a predetermined interval by a connecting flange 150D.

The connecting flange 150D has a cylindrical body portion 150D1 and two flange portions 150D2 extending radially outward from both axial ends of the body portion 150D1. Each flange portion 150D2 is provided with a through hole for bolt fixing at a position corresponding to the tapped hole provided in the mounting surface of the load side bracket 150B3 and the second bracket 150A4. It is fixed to the bracket 150A4 with bolts.

Note that the servo motor unit 150 includes two rotary encoders (one built in the second bracket 150A4 of the two-axis output servo motor 150A, and one built in the second bracket 150A4 of the servo motor 150B, and a rotary encoder built in the second bracket 150A4 of the servo motor 150B A rotary encoder 150B5) attached to the bracket 150B4 is provided, but normally only one rotary encoder is used for drive control of the servo motor unit 150, and the other rotary encoder is used for maintenance and monitoring of the drive state.

For example, in order to perform a vibration test or a power transmission device durability test (rotational torsion test), a large shaft torque that fluctuates at high speed (high frequency) is required. In order to generate such a large torque that fluctuates at a high frequency, a motor with a small rotor moment of inertia (inertia) and a large capacity (high output) is required. To realize such a servo motor, it is necessary to make the rotor elongated. However, if the rotor is elongated beyond a certain point, the rigidity of the rotor (rotating shaft) decreases, and vibrations of the rotor that warp into an arch shape become noticeable, making it impossible for the motor to operate normally. Therefore, with 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.

In the servo motor unit 150 of this embodiment, a long rotor connected by a coupling 150C is supported by bearings at four locations in total: at both ends in the longitudinal direction and at two locations near the connection portion. Even if the rotor becomes longer, it remains highly rigid and operates stably, making it possible to generate large torque that fluctuates at high frequencies, which was impossible with conventional servo motors. Became. For example, the servo motor unit 150 alone (in a no-load state) can achieve an angular acceleration of 30,000 rad/s ² or more.

The servo motor unit 150 of this embodiment has a configuration in which two servo motors (two motor cases and two rotating shafts) are connected, but as shown in FIG. One or more bearings may be provided midway in the longitudinal direction, and the drive shaft may be pivotally supported at one or more locations at both ends and midway.

Next, the configuration of the rotary torsion testing device 1 according to the first embodiment of the present invention will be described. FIG. 4 is a side view of the rotary torsion testing device 1 according to the first embodiment of the present invention. The rotational torsion test device 1 is a device that performs a rotational torsion test using an automobile clutch as a specimen T1, and tests the input shaft and output shaft (for example, clutch cover and clutch disc) of the specimen T1 while rotating the specimen T1. A fixed or variable torque set between can be applied. The rotary torsion testing device 1 includes a pedestal 10 that supports each part of the rotary torsion testing device 1, a load applying section 100 that applies a predetermined torque to the specimen T1 while rotating together with the specimen T1, and a load applying section 100 that is rotatable. bearing parts 20, 30, and 40 that support the bearing parts 20, 30, and 40; slip ring parts 50 and 60 that electrically connect the inside and outside of the load applying part 100; a rotary encoder 70 that detects the rotation speed of the load applying part 100; 100, an inverter motor 80, a drive pulley 91, and a drive belt (timing belt) 92 are provided.

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

FIG. 5 is a longitudinal cross-sectional view of the load application section 100 of the rotary torsion testing apparatus 1. The load applying section 100 includes a stepped cylindrical casing 100a, a servo motor unit 150 installed in the casing 100a, a reduction gear 160, a connecting shaft 170, and a torque sensor 172. The casing 100a includes a motor accommodating part (body part) 110 in which a servo motor unit 150 is housed, a shaft part 120 rotatably supported by a bearing part 20, and a shaft part 130 rotatably supported by a bearing part 30. and a shaft portion 140 to which the slip ring 51 of the slip ring portion 50 (FIG. 4) is attached. The motor accommodating portion 110 and the shaft portions 120, 130, and 140 are substantially cylindrical members (or stepped cylindrical members whose diameters change stepwise in the axial direction) each having a hollow portion. The motor accommodating portion 110 is a member with the largest outer diameter that accommodates the servo motor unit 150 in a hollow portion. A shaft portion 120 is connected to one end portion (right end portion in FIG. 5) of the motor accommodating portion 110 on the specimen T1 side, and a shaft portion 130 is connected to the other end portion. Further, a shaft portion 140 is connected to an end of the shaft portion 130 on the opposite side from the motor accommodating portion 110 . The shaft portion 140 is rotatably supported by the bearing portion 40 at the tip portion (left end portion in FIG. 4).

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

A drive shaft 152 of the servo motor unit 150 is connected to an input shaft of a reduction gear 160 via a coupling 154. Further, a connecting shaft 170 is connected to the output shaft of the reducer 160. Note that the reducer 160 includes a mounting flange 162, and with the mounting flange 162 sandwiched between the motor housing part 110 and the shaft part 120, the motor housing part 110 and the shaft part 120 are connected by bolts (not shown). By tightening, the reducer 160 is fixed to the casing 100a.

The shaft portion 120 is a substantially stepped cylindrical member, and has a pulley portion 121 with a large outer diameter on the motor housing portion 110 side, and a main shaft portion 122 rotatably supported by a bearing portion 20 on the specimen T1 side. has. As shown in FIG. 4, a drive belt 92 is wound around the outer peripheral surface of the pulley portion 121 and a drive pulley 91 attached to the drive shaft 81 of the inverter motor 80, and the drive force of the inverter motor 80 is The load is transmitted to the pulley section 121 by the drive belt 92, and the load applying section 100 is rotated. Furthermore, a connecting portion between the reducer 160 and the connecting shaft 170 is accommodated within the pulley portion 121 . A compact device structure can be realized without increasing the number of parts by using the part where the outer diameter needs to be increased to accommodate this connection part as a pulley.

A torque sensor 172 is attached to the tip of the main shaft portion 122 of the shaft portion 120 (the right end portion in FIG. 5). Further, one surface of the torque sensor 172 (the right side in FIG. 5) is a seating surface to which the input shaft (clutch cover) of the specimen T1 is attached, and the torque applied to the specimen T1 is detected by the torque sensor 172. .

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 rotatably supported within the shaft portion 120 by bearings 123 and 124. The torque sensor 172 is formed into a substantially cylindrical shape with 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 projects to the outside. The tip protruding from the torque sensor 172 is inserted and fixed into a shaft hole of a clutch disc (clutch hub) that is the output shaft of the specimen T1. That is, by rotating the connecting shaft 170 with respect to the casing 100a of the load applying section 100 by the servo motor unit 150, the input shaft (clutch cover) of the specimen T1 fixed to the casing 100a is fixed to the connecting shaft 170. A set dynamic or static torque can be applied between the output shaft (clutch disc) of the specimen T1 and the output shaft (clutch disc).

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

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

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. Further, the brush 53 is fixed to the bearing section 40 by a brush fixture 52. The slip ring 51 has four electrode rings 51r arranged at equal intervals in the axial direction, and each brush 53 is arranged facing each electrode ring 51r. Each power line 150W of the servo motor unit 150 is connected to each electrode ring 51r, and each brush 53 is connected to a servo motor drive unit 330 (described later). That is, each power line 150W of the servo motor unit 150 is connected to the servo motor drive unit 330 via the slip ring portion 50. The slip ring section 50 introduces the drive current of the servo motor unit 150 supplied by the servo motor drive unit 330 into the rotating load application section 100 .

Further, a slip ring (not shown) of the slip ring portion 60 is attached to the tip portion (left end portion in FIG. 4) of the shaft portion 140. A communication line 150W' (FIG. 5) extending from the servo motor unit 150 is connected to the slip ring of the slip ring section 60, and is connected to, for example, a torque sensor 172 or a rotary encoder 150B5 (FIG. 2) built in the servo motor unit 150. ) etc. are outputted to the outside via the slip ring section 60. When a large current such as a drive current for a large-capacity motor is passed through a slip ring, large electromagnetic noise is likely to be generated due to discharge. Additionally, slip rings are not well shielded and are therefore susceptible to electromagnetic noise interference. As mentioned above, the configuration connects the communication line 150W' through which a weak current flows and the power line 150W through which a large current flows to external wiring using separate slip rings placed a certain distance apart. Mixing of noise into communication signals is effectively prevented. Further, in this embodiment, the slip ring portion 60 is provided on the surface of the bearing portion 40 on the opposite side to the slip ring portion 50 side. With this configuration, the effect of shielding the slip ring part 60 from electromagnetic noise generated in the slip ring part 50 by the bearing part 40 can also be obtained.

Next, the control system of the rotary torsion testing device 1 will be explained. FIG. 6 is a block diagram showing a schematic configuration of the control system of the rotary torsion testing device 1. As shown in FIG. The rotary torsion test apparatus 1 includes a control unit C1 that controls the entire rotary torsion test apparatus 1, a setting unit 370 for setting test conditions, and a control unit 370 for setting test conditions (waveforms of torque and torsion angle applied to the specimen). a waveform generation unit 320 that calculates the waveform of the drive amount of the servo motor unit 150 based on the following information and outputs it to the control unit C1; and a servo motor that generates the drive current of the servo motor unit 150 based on the control of the control unit C1. A drive unit 330, an inverter motor drive unit 340 that generates a drive current for the inverter motor 80 based on the control of the control unit C1, and a torque measurement unit that calculates the torque being applied to the specimen based on the signal of the torque sensor 172. unit 350 and a rotation speed measuring unit 360 that calculates the rotation speed of the load applying section 100 based on the signal from the rotary encoder 70.

The setting unit 370 includes a user input interface such as a touch panel (not shown), a replaceable recording media reader such as a CD-ROM drive, an external input interface such as a GPIB (General Purpose Interface Bus) or a USB (Universal Serial Bus), and Equipped with a network interface. The configuration unit 370 receives user input via a user input interface, data read from a removable recording medium, data input from an external device (for example, a function generator) via an external input interface, and/or a network interface. The test conditions are set based on the data obtained from the server via the . Note that the rotational torsion testing apparatus 1 of the present embodiment allows the torsion applied to the specimen T1 to be applied to the specimen T1 at a torsion angle (i.e., a servo motor unit detected by a rotary encoder 150B5 built in the servo motor unit 150). Two control methods are supported: displacement control, which is controlled based on the drive amount of 150), and torque control, which is controlled based on the torque applied to the specimen T1 (that is, detected by the torque sensor 172). , the setting unit 370 can set which control method is to be used for control.

The control unit C1 instructs the inverter motor drive unit 340 to rotate the inverter motor 80 based on the set value of the rotational speed of the specimen T1 acquired from the setting unit 370. Furthermore, the control unit C1 instructs the servo motor drive unit 330 to drive the servo motor unit 150 based on the waveform data of the drive amount of the servo motor unit 150 acquired from the waveform generation unit 320.

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

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

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

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

In the rotational torsion testing device 1 described above, the output of the inverter motor 80 for rotational speed control and the output of the servo motor unit 150 for torque control are combined, making it possible to control the rotational speed and torque independently and with high precision. It is configured. In particular, by newly adopting a servo motor unit 150 in which multiple ultra-low inertia servo motors are connected in series, it is possible to control large torques that fluctuate with high angular jerk (angular jerk), making it possible to control large torques that vary with high angular jerk (angular jerk). It is now possible to accurately reproduce the output (especially the torque vibration of a reciprocating engine). Further, by using the servo motor unit 150, the responsiveness of torque control is also improved, and a response time of 3 ms or less is achieved. A rotary drive device having such a configuration can be used not only as a rotary torsion testing device but also as a power source for various devices. In particular, in a testing 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. Further, since the torque generated by the servo motor unit 150 is controlled with high precision, the reproducibility is extremely high and there is no individual difference. Therefore, it is possible to apply a more uniform load than in conventional tests using an actual engine, making it possible to perform tests with higher reproducibility.

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

The power simulator 1a shown in FIG. 7 differs from the rotational torsion testing device 1 described above in that it includes a bearing portion 1020, a slip ring 1401, and a mounting portion 173. The bearing section 1020 has the same configuration as the bearing section 1020 of the second embodiment described later, and includes a built-in 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 section 1020 and extracts a signal output from a torque sensor built into the bearing section 1020 to the outside. Further, the attachment portion 173 is a flange joint, and is attached to the tip of the connecting shaft 170. The power simulator 1a configured in this manner includes engine auxiliary equipment (for example, damper pulley, alternator, balance shaft, starter motor, ring gear, water pump, oil pump, chain, timing belt, coupling, VCT), Used for durability tests of power transmission devices, tires, etc.

Furthermore, the rotary torsion test device 1 and the power simulator 1a described above have a two-tiered structure in which the inverter motor 80 is placed on the lower base plate 11 and the load applying section 100 is placed on the upper base plate 12. However, like the power simulator 1b shown in FIG. 8, it may be a single-stage structure in which the inverter motor 80 and the load applying section 100 are arranged on the same base plate 10X. Note that the two-tiered structure is effective in reducing the installation area. Moreover, the single-stage structure is advantageous in reducing costs because of its simple structure, and is also advantageous in improving the rigidity of the base (that is, vibration resistance characteristics and load resistance characteristics).

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

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

As shown in FIGS. 9 and 10, the test apparatus 100E is a power simulator 1a in which a support section S for holding a specimen is added. That is, the test apparatus 100E has an inverter motor 80 attached to the lower base plate 11 of the gantry 10, and a load applying unit 100 rotatably supported by bearings 1020, 30, and 40 attached to the upper base plate 12. We are prepared. The load applying section 100 is rotationally driven by an inverter motor 80. The load application section 100 has a built-in servo motor unit 150 and a reduction gear, and the output shaft of the servo motor unit 150 is connected to a connecting shaft 170 that projects outside of the load application section 100 via the reduction gear. The connecting shaft 170 is disposed coaxially with the rotation axis of the load applying section 100, and the rotation of the connecting shaft 170 is the rotation of the load applying section 100 by the inverter motor 80 plus the rotation of the servo motor unit 150. . The inverter motor 80 reproduces the rotational speed of the engine, and the servo motor unit 150 reproduces the high-speed fluctuating torque (high angular acceleration, high angular jerk (angular jerk)) of the engine.

At the tip of the connecting shaft 170 of the load applying section 100, a mounting section 173 for mounting the ring gear T1 is attached. Furthermore, a support portion S that supports the starter motor T2 is attached to the upper base plate 12 of the gantry 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 test is performed by driving the power simulator 1a of the test device 100E to apply rotation simulating the rotation of the engine to the ring gear T1 and the starter motor T2.

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

As shown in FIG. 11, the rotary torsion test device 1000 has four bases 1011, 1012, 1013, and 1014 that support each part of the rotary torsion test device 1000, and the two ends of the test specimen T2 while rotating together with the specimen T2. a load application section 1100 that applies a predetermined torque to the load application section 1100, bearing sections 1020, 1030, and 1040 that rotatably support the load application section 1100, and a slip ring section 1050 that electrically connects the internal and external wiring of the load application section 1100; 1060 and 1400, a rotary encoder 1070 that detects the rotation speed of the load application section 1100, and a rotary encoder 1070 that rotates the load application section 1100 and one end of the specimen T2 (the right end in FIG. 11) in a set rotation direction and rotation speed. an inverter motor 1080 that transmits the driving force of the inverter motor 1080 to the load applying unit 1100 (drive pulley 1191, drive belt (timing belt) 1192, and driven pulley 1193), It includes a driving force transmitting section 1200 that transmits the force to one end of the specimen T2. The driving force transmission section 1200 includes a bearing section 1210, a drive shaft 1212, a relay shaft 1220, a bearing section 1230, a drive shaft 1232, a drive pulley 1234, a bearing section 1240, a drive shaft 1242, a driven pulley 1244, and a drive belt (timing belt) 1250. and a workpiece attachment part 1280.

The bearing parts 1020, 1030, 1040, slip ring part 1050, slip ring part 1060, rotary encoder 1070, inverter motor 1080, and drive pulley 1091 in the rotary torsion test apparatus 1000 are the same as the rotary torsion test apparatus 1 of the first embodiment, respectively. The bearing parts 20, 30, 40, the slip ring part 50, the slip ring part 60, the rotary encoder 70, the inverter motor 80, and the drive pulley 91 are configured in the same manner as in Further, the load applying section 1100 has the same configuration as the load applying section 100 of the first embodiment, except for a shaft section 1120, a connecting shaft 1170, a workpiece mounting section 1180, and a slip ring section 1400, which will be described later. Further, the drive belt 1192 differs in configuration from the drive belt 92 of the first embodiment in that it is hooked on a driven pulley 1193 on the driven side, but the other configurations are the same as the drive belt 92. In the following description of the second embodiment, the same or similar symbols will be used for the same or similar configurations as in the first embodiment, detailed explanations will be omitted, and differences in configuration from the first embodiment will be explained. I will mainly explain.

The four bases 1011, 1012, 1013, and 1014 are each placed on the same flat floor F and fixed with fixing bolts (not shown). An inverter motor 1080 and a bearing section 1210 are fixed on the base 1011. Bearing sections 1020, 1030, and 1040 that support the load applying section 1100 and a support frame 1402 of the slip ring section 1400 are fixed on the base 1012. Further, a bearing portion 1230 is fixed to the base 1013, and a bearing portion 1240 is fixed to the base 1014. The bases 1013 and 1014 are movable in the axial direction of the bearing portion 1230 or 1240 depending on the length of the specimen T1 by loosening the respective fixing bolts.

The connecting shaft 1170 of the load applying section 1100 protrudes outward from the tip (right end in FIG. 13) of the shaft 1120, and a workpiece attachment section (flange joint) is provided at the tip (right end in FIG. 13) of the connecting shaft 1170. ) 1180 is fixed. A slip ring 1401 having a plurality of electrode rings is attached to the axial center of the portion of the connecting shaft 1170 that protrudes from the shaft portion 1120.

Further, as shown in FIG. 13, an annular narrowed portion 1172 having a narrow outer diameter is formed in the portion of the connecting shaft 1170 accommodated in the shaft portion 1120, and the circumferential surface of the narrowed portion 1172 is A strain gauge 1174 is attached. Further, the connecting shaft 1170 is a cylindrical member having a hollow portion (not shown) that passes through the central axis, and the narrowed portion 1172 has an insertion hole (not shown) that communicates with the hollow portion. 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 are connected to each electrode ring of the slip ring 1401. Note that instead of the hollow part and the insertion hole, a wiring groove extending from the narrowed part 1172 to the slip ring 1401 is provided on the circumferential surface of the connecting shaft 1170, and the leads of the strain gauge 1174 are routed through the wiring groove to the slip ring 1401. It may also be a configuration.

A brush portion 1403 fixed on a support frame 1402 is arranged at the bottom of the slip ring 1401. The brush portion 1403 includes a plurality of brushes arranged to face each other so as to be in contact with each electrode ring of the slip ring 1401, respectively. The terminal of each brush is connected to a torque measurement unit 1350 (described later) by a wire (not shown).

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

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

(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 parallel to each other, are connected by drive belts 1192 and 1250, respectively, and a power circulation system is configured. There is. However, the present invention is not limited to this configuration, and the scope of the present invention also includes configurations in which power is transmitted using a gear device instead of a drive belt, as in the third to seventh embodiments described below. It will be done.

FIG. 14(a) is a top view of a torsion testing device according to a third embodiment of the present invention. Moreover, FIG. 14(b) is a side view of the torsion test device according to this embodiment. As shown in FIG. 14, in the torsion testing apparatus 100 of this embodiment, a work rotation servo motor 121, a torque applying unit 130, a first gear box 141, and a second gear box 142 are fixed on a base 110. The structure is as follows.

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

A drive pulley 122 is attached to the output shaft 121a of the work rotation servo motor 121. Further, the shaft 123a of the driven pulley 123 is attached to the shaft connecting portion 141a1 of the first gear box 141. Furthermore, an endless belt 124 is hung between the drive pulley 122 and the driven pulley 123, and by driving the work rotation servo motor 121, the driven pulley 123 can be rotated at a desired rotation speed. .

A torque applying unit 130 is connected to the shaft connecting parts 141b1 and 141b2. The configuration of the torque applying unit 130 will be described below.

FIG. 15 is a side sectional view of the torque applying unit 130 and the first gearbox 141 of this embodiment. The torque applying unit 130 includes a casing 131 , a torque applying servo motor unit 132 fixed within the casing 131 , and a speed reducer 133 . Note that 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 is used alone instead of the servo motor unit 150. Good too. A tubular portion 131a is formed at one axial end of the casing 131 (on the right side in the figure). The tubular portion 131a is inserted into the first gearbox 141 via the shaft connection portion 141b1, and is rotatably supported within the first gearbox 141. Further, a gear 141b3 is attached to the tubular portion 131a.

The reducer 133 has an input shaft 133a and an output shaft 133b, and decelerates 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 applying servo motor unit 132 by a coupling 134. Further, 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 of the tubular portion 131a. The output shaft 133b of the reducer 133 protruding from the tubular portion 131a is connected to the shaft connecting portion 141b2 of the first gearbox 141.

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

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

Here, the shaft 123a of the driven pulley 123 attached to the shaft connection part 141a1 of the first gearbox 141 and the shaft attached to the shaft connection part 141a2 are connected inside the first gearbox 141 via a coupling 153. They are connected to each other so that they rotate together. Further, a gear 141a3 is attached to the shaft 123a of the driven pulley 123 attached to the shaft connecting portion 141a1. A gear 141b3 is mounted inside the first gearbox 141 to the tubular portion 131a connected to the shaft connection portion 141b1. As shown in FIG. 14(a), the gear 141a3 and the gear 141b3 mesh with each other via the intermediate gear 141i, and the shaft connected to the shaft connection parts 141a1 and 141a2 and the shaft connected to the shaft connection part 141b1. Rotational motion can be transmitted between them. Note that since the intermediate gear 141i is interposed between the gear 141a3 and the gear 141b3, the driven pulley 123, the relay shaft 143, and the casing 131 of the torque applying unit 130 rotate in the same direction.

A gear 142a1 is attached to the shaft portion (one end portion of the relay shaft 143) connected to the shaft connection portion 142a. Further, 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 via the intermediate gear 142i inside the second gearbox 142, and between the shaft connected to the shaft connection part 142a and the shaft connected to the shaft connection part 142b, Rotational motion can be transmitted to each other. Note that since the intermediate gear 142i is interposed between the gear 142a1 and the gear 142b1, the shaft connected to the shaft connection part 142a and the shaft connected to the shaft connection part 142b are rotated in the same direction. It has become.

Therefore, in this embodiment, when the work rotation servo motor 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 rotationally driven. It turns out. As described above, since the torque applying servo motor unit 132 is fixed to the casing 131, the casing 131 and the torque applying servo motor rotate together. Therefore, when the servo motor unit 132 for applying torque is driven while the casing 131 is rotating, the output shaft 133b of the reducer 133 changes depending on the rotational speed of the casing 131 and the servo motor unit 132 for applying torque. It will rotate at the rotation speed that is the sum of the rotation speed.

Transmission unit W2 is of the same type as transmission unit W1 (same reduction ratio). Further, the gear ratios of the gear boxes 141 and 142 are both 1:1. Therefore, the rotational speeds of the shafts connected to the shaft connecting portions 141a2 and 141b2 of the first gearbox 141 are approximately equal. Note that the transmission unit W2 is a type of dummy work used to adjust the rotation speed of the shafts connected to the shaft connecting portions 141a2 and 141b2 as described above, and is not subject to the torsion test.

In this embodiment, for example, the input shaft W1a of the transmission unit W1 is driven by driving the workpiece rotation servo motor 121 at a constant speed and reciprocating the output shaft 132a by the torque applying servo motor unit 132 (FIG. 15). It becomes possible to apply periodically varying torque while rotating.

(Fourth embodiment)
Next, a fourth embodiment of the present invention will be described. FIG. 16 is a top view of a torsion testing device according to a fourth embodiment of the present invention. As shown in FIG. 16, the torsion test device 100A of this embodiment does not use a dummy work, and the coupling 152 and the shaft connection part 142a of the second gearbox 142 are directly connected by the relay shaft 143A. It is the same as the torsion test device 100 of the third embodiment except for. In addition, 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 numerals, and redundant description will be omitted.

In this embodiment, the rotation speed of the relay shaft 143A (i.e., the rotation speed of the casing 131 of the torque applying unit 130) and the rotation speed of the shaft connected to the shaft connection part 141b2 of the first gearbox 141 (i.e., the transmission The number of rotations of the input shaft W1a of the unit W1 is different. Therefore, in this embodiment, the torque applying servo motor unit 132 (FIG. 15) of the torque applying unit 130 is rotationally driven so as to compensate for the change in the rotation speed of the input/output shaft of the transmission unit W1. For example, if the reduction ratio of the transmission unit W1 is 1/3.5, and a torsion test is performed with the rotation speed of the input shaft W1a being 4000 rpm and the rotation speed of the output shaft W1b being 1143 rpm, the torque applying unit 130 is rotated at 1143 rpm. The rotation speed of the work rotation servo motor 121 is set so that torque is applied to the casing 131, and the rotation speed of the servo motor unit 132 is set so that the relative rotation speed of the output shaft 133b of the reducer 133 with respect to the casing 131 is 2857 rpm. By setting , the rotation speed of the input shaft W1a of the transmission unit W1 can be set to 4000 rpm.

In this manner, in this embodiment, it is possible to perform a torsion test on the transmission unit W1 without using a dummy work while performing power circulation.

In addition, in this embodiment, since the highly responsive servo motor drives the rotation of the workpiece and applies torque, it is also possible to change the gear ratio of the transmission unit W1 while performing the torsion test. be. That is, in the present embodiment, it is possible to suddenly change the rotation speed of the torque applying servo motor unit 131 in synchronization with a change in the rotation speed of the output shaft W1b due to a change in the gear ratio of the transmission unit W1. Even if the gear ratio of the unit W1 is changed, the gears in the gearboxes 141 and 142 and the transmission unit W1 will not be damaged due to excessive load.

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

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

In the torsion test apparatus 100B of this embodiment, since the output shaft of the differential gear DG1 is two systems (DG1a, DG1b), the second gearbox (142B1, 142B2) is used to return the output of the differential gear DG1 to the first gearbox 141B. ) and two relay shafts (143B1, 143B2) are provided. Specifically, output shafts DG1a and DG1b of differential gear DG1 are connected to relay shafts 143B1 and 143B2 via second gear boxes 142B1 and 142B2, respectively.

The first gearbox 141B also includes shaft connecting portions 141Bb1 and 141Bb2 (shaft connecting portions 141b1 and 141b2 of the third embodiment) to which the tubular portion 131a of the casing 131 of the torque applying unit 130 and the input shaft TR1a of the transmission unit TR1 are attached, respectively. In addition to the shaft connection parts 141Ba1 and 141Ba2 to which the output shaft 121a of the work rotation servo motor 121 and the relay shaft 143B1 are connected, the shaft connection part 143Bc is connected to the relay shaft 143B2. Further, the output shaft 121a of the work rotation servo motor 121 and the relay shaft 143B1 are connected via a coupling 153B disposed within the first gear box 141. Further, 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 disposed within the first gearbox 141.

The shafts connected to the shaft connecting parts 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 applying unit 130 are configured to rotate.

In this embodiment, as in the fourth embodiment, since the rotation speed of the input shaft TR1a of the transmission unit TR1 and the rotation speed of the relay shafts 143B1 and 143B2 are different, the torque applying motor is 131 (FIG. 15).

(Sixth embodiment)
Further, in the configuration of the present invention, it is also possible to use a power transmission system for a front-wheel drive vehicle as a workpiece. A torsion test device according to a sixth embodiment of the present invention, which will be described below, performs a torsion test on a power transmission system of a front-wheel drive vehicle.

FIG. 18 is a top view of a torsion test device 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 using 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, as a workpiece. It is something to do.

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

The first gearbox 141C of this embodiment, like the fifth embodiment, includes shaft connection parts 141Cb1 and 141Cb2 to which the tubular part 131a of the casing 131 of the torque applying unit 130 and the input shaft TR2a of the transmission unit TR2 are attached, respectively, and a workpiece. It has shaft connection parts 141Ca1 and 141Ca2 to which the output shaft 121a of the rotation servo motor 121 and the output shaft DG2a of the differential gear DG2 are connected, and a shaft connection part 143Cc to be connected to the relay shaft 143C. The output shaft 121a of the work rotation servo motor 121 and the output shaft DG2a of the differential gear DG2 are connected by a coupling 153C disposed in the first gear box 141C. Further, the output shaft 133b of the reducer 133 of the torque applying unit 130 and the input shaft TR2a of the transmission unit TR2 are connected by a coupling 151C disposed within the first gearbox 141C.

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

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

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

In the torsion test apparatus 100B of this embodiment, since the output shaft of the differential gear DG1 is two systems (DG1a, DG1b), the second gearbox (142B1, 142B2) is used to return the output of the differential gear DG1 to the first gearbox 141B. ), two systems each of bevel gearboxes (144B1, 144B2) and relay shafts (143B1, 143B2) are provided. Specifically, output shafts DG1a and DG1b of differential gear DG1 are connected to relay shafts 143B1 and 143B2 via second gearboxes 142B1 and 142B2 and bevel gearboxes 144B1 and 144B2, respectively.

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

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

In this embodiment, since the rotation speed of the input shaft DG1c of the differential gear DG1 and the rotation speed of the output shafts DG1a and DG1b are different, the servo motor unit built in the torque applying unit 130 is configured to compensate for this difference in rotation speed. A rotation speed of 150 is controlled.

(Eighth embodiment)
Furthermore, the present invention can also be applied to a test device for power transmission devices for front-wheel drive vehicles. The torsion testing device according to the eighth embodiment of the present invention, which will be described below, is a power circulation type testing device that performs a rotational torsion test on the power transmission system of a front-wheel drive vehicle.

FIG. 20 is an external view of a torsion test device 100C according to the 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 front-wheel drive vehicle.

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

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

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

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 testing 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. It is also possible to apply the present invention to various tests of tires, as in the ninth and tenth embodiments of the present invention described below.

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

The first gearbox 141D includes four shaft connections 141Da1, 141Da2, 141Db1, and 141Db2. Further, the second gearbox 142D includes two shaft connection parts 142Da and 142Db.

In this embodiment, both ends of the shaft 145, which is the rotation axis of the rotating drum DR serving as a simulated road surface, are connected to the shaft connection portion 141Da2 of the first gearbox 141D and the shaft connection portion 142Da of the second gearbox 142D, respectively. ing. Further, both ends of a shaft 144 serving as a rotation axis of the tire T, which is the subject, are connected to a shaft connecting portion 141Db2 of a first gearbox 141D and a shaft connecting portion 142Db of a second gearbox 142D, respectively.

Similar to the second embodiment, the rotation of the output shaft 121a of the work rotation servo motor 121 for driving the tire T and the rotating drum DR is performed by a belt mechanism composed of a drive pulley 122, a driven pulley 123, and an endless belt 124. Through this, the shaft 123a of the driven pulley 123 is rotationally driven. The shaft 123a is connected to the shaft connecting portion 141a of the first gearbox 141D.

The tubular portion 131a of the casing 131 of the torque applying unit 130 is connected to the shaft connecting portion 141Db1 of the first gearbox 141D. Further, the output shaft 133b of the speed reducer 133 of the torque applying unit 130 is connected to one end of the shaft 144 for the tire T via a coupling 151D disposed inside the first gearbox 141D.

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

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

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

With the above configuration, by driving the rotational servo motor 121, it is possible to rotationally drive the rotating drum DR and the tires T while performing power circulation. In addition, as shown in FIG. 21, in this embodiment, since the diameters of the rotating drum DR and the tires T are different, the gear ratios in the first gear box 141D and the second gear box 142D are different from that of the rotating drum DR and the tires T. The value is set according to the ratio of the diameters of the

In the tire wear test device having the configuration described above, the tire T and the rotating drum DR are rotated by setting the tire T on the shaft 144 and driving the rotating servo motor 121. In this state, the torque applying servo motor unit 131 (FIG. 2) of the torque applying unit 130 is driven to apply torque in the forward or reverse direction to the tire T, thereby simulating the acceleration and deceleration of the automobile. It becomes possible to conduct the test.

(10th embodiment)
Another example in which the present invention is applied to tire testing will be introduced. A tire testing device according to a tenth embodiment of the present invention, which will be described below, is a testing device that performs tire wear tests, durability tests, running stability tests, and the like.

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

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

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

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

The alignment control mechanism 160 of this embodiment supports the tire T as a test specimen mounted on a wheel, presses the tread portion against the simulated road surface of the rotating drum 10, and controls the alignment of the tire T with respect to the simulated road surface. This is a mechanism that adjusts the load (ground pressure) to a set state. The alignment control mechanism 160 includes a tire load adjustment section 161 that adjusts the tire load by moving the position of the rotation axis of the tire T in the radial direction of the rotary drum 10, and a tire load adjustment section 161 that adjusts the tire load by moving the position of the rotation axis of the tire T in the radial direction of the rotary drum 10. a slip angle adjustment section 162 that adjusts the slip angle of the tire T with respect to a simulated road surface; a camber angle adjustment section 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; A traverse device 164 is provided to move the T in the direction of the rotation axis.

By setting the tire T in the tire testing device 100D having the configuration described above and driving the rotational drive inverter motor 80, the tire T and the rotating drum 10 rotate at the same circumferential speed. In this state, the servo motor unit 150 of the torque applying unit 130 is driven to apply driving force and braking force to the tire T, thereby simulating the actual driving conditions for tire wear tests, durability tests, and driving stability. It becomes possible to conduct tests, etc.

(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.

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

The test device 100F includes a power simulator 100X that includes an inverter motor 80 and a load application section 100 that includes a servo motor unit 150, a support section S that supports the case of the FR transmission T that is the test specimen, and a torque sensor 172a. , 172b, and two power absorption servo motors 90A and 90B. The input shaft of the FR transmission T is connected to the output shaft of the load applying section 100 via the torque sensor 172a. Further, the output shaft To of the FR transmission T is connected to the pulley section 180 via the torque sensor 172b. Note that the torque sensors 172a, 172b have the same configuration as the torque sensors 172a, 172b, 172c of the seventh embodiment.

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

(12th embodiment)
FIG. 25 is an external view of a power absorption type durability testing device 100G for FF transmission according to the twelfth embodiment of the present invention.

The FF transmission TR, which is a specimen, includes 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 section 100 via the torque sensor 172a. Further, the output shaft TRb (TRc) of the FF transmission TR is connected to a power absorption servo motor 90B (90C) via a torque sensor 172b (172c), a pulley portion 180b (180c), and a drive belt. The power absorption servo motor 90B (90C) applies a load to the output shaft TRb (TRc) of the FF transmission TR. Note that the torque sensors 172a, 172b, and 172c have the same configuration as the torque sensors 172a, 172b, and 172c of the seventh embodiment.

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

First, the structure of the first drive section 3110 will be explained. FIG. 27 is a partially cutaway side view of the first drive section 3110. The first drive 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 arranged horizontally on the top of the base 3110b. It is assembled on a movable plate 3111. The servo motor unit 150 is the same as in the first embodiment. The servo motor unit 150 is fixed on the movable plate 3111 with its output shaft (not shown) oriented in the horizontal direction. Furthermore, the movable plate 3111 of the base 3110b is provided so as to be slidable in the direction of the output shaft of the servo motor unit 150 (the left-right direction in FIG. 26).

The output shaft (not shown) of the servo motor unit 150 is connected to the 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 the spindle 3115. The spindle 3115 is rotatably supported by a bearing 3114a fixed to a frame 3114b of the case 3114. A chuck device 3116 is fixed to the other end of the spindle 3115 for attaching one end (one of the rotating shafts) of the specimen T1 to the first drive section 3110. 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 transferred to one end of the specimen T1 via the torque sensor 3117, spindle 3115, and chuck device 3116. It is meant to be transmitted. Further, a rotary encoder (not shown) is attached to the spindle 3115 to detect the rotation angle of the spindle 3115.

As shown in FIG. 27, the reducer 3113 is fixed to the frame 3114b of the case 3114. Further, the reducer 3113 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 the power transmission shaft from the reducer 3113 to the chuck device 3116, and also functions as a device frame that rotatably supports this power transmission shaft at the positions of the reducer 3113 and the spindle 3115. 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 attached to the frame 3114b of the case 3114 via bearings. Supported. Therefore, only the test load (torsion load) is applied to the torque sensor 3117 without the bending moment due to the gear mechanism of the reducer 3113 or the weight of the spindle 3115 (and chuck device 3116), so it can detect the test load with high accuracy. can do.

A plurality of slip rings 3119a are formed on the cylindrical surface of one end 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 ring 3119a from the outer peripheral side. A plurality of brushes 3119b are attached to the inner periphery of the brush holding frame 3119c, each of which contacts a corresponding slip ring 3119a. When the servo motor unit 150 is driven and the torque sensor 3117 is rotating, the brush 3119b slips on the slip ring 3119a while maintaining contact with the slip ring 3119a. The output signal of the torque sensor 3117 is configured to be output to a slip ring 3119a, and the output signal of the torque sensor 3117 can be taken out to the outside of the first drive unit 3110 via a brush 3119b that contacts the slip ring 3119a. It has become.

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

The torsion test device 3100 of the present embodiment has a chuck device of a first drive section 3110 and a second drive section 3120, respectively, to connect an output shaft O and an input shaft I (engine side) of a specimen T1, which is a transmission unit for an FR vehicle. 3116 and 3126, and are rotated synchronously by servo motor units 150 and 150, and by making a difference in the rotational speed (or rotational phase) of both chuck devices 3116 and 3126, the sample T1 is It applies torsional load. For example, the chuck device 3126 of the second drive unit 3120 is rotated at a constant speed, and the chuck device 3116 is rotationally driven so that the torque detected by the torque sensor 3117 of the first drive unit 3110 varies according to a predetermined waveform. Periodically varying torque is applied to the specimen T1, which is a transmission unit.

In this way, the torsion testing device 3100 of the present embodiment is capable of precisely driving both the input shaft I and the output shaft O of the transmission unit with the servo motor units 150, 150, so that the transmission unit can be rotationally driven. By applying varying torque to each shaft of the transmission unit while the vehicle is moving, the test can be conducted under conditions close to the actual driving conditions of the vehicle.

When performing a rotational torsion test on a device such as a transmission unit in which an input shaft I and an output shaft O are connected via a gear or the like, the magnitudes of the torques applied to the input shaft I and the output shaft O do not necessarily match. Therefore, in order to more accurately understand the behavior of the 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 in both the first drive section 3110 and the second drive section 3120 as described above, the input shaft I side and the output shaft O side of the transmission unit (specimen T1) Torque can be measured individually with and.

In addition, in the above example, the input shaft I side of the transmission unit is driven to rotate at a constant speed, and the output shaft O side is configured to apply torque, but the present invention is not limited to the above example. That is, a configuration may be adopted in which the output shaft O side of the transmission unit is driven to rotate at a constant speed, and variable torque is applied to the input shaft I side. Alternatively, a configuration may be adopted in which both the input shaft I side and the output shaft O side of the transmission unit are driven to rotate at varying rotational speeds. Alternatively, a configuration may be adopted in which only the torque of each axis is controlled without controlling the rotation speed. Alternatively, a configuration may be adopted in which the torque and rotational speed are varied according to a predetermined waveform. The torque and rotation speed can be varied according to an arbitrary waveform generated by a function generator, for example. Furthermore, the torque and rotational speed of each axis of the specimen T1 can also be controlled based on the waveform data of the torque and rotational speed measured in an actual running test.

The torsion testing apparatus 3100 of this embodiment is capable of adjusting the interval between the chuck devices 3116 and 3126 so as to be compatible with transmission units of various sizes. Specifically, a movable plate drive mechanism (not shown) allows the movable plate 3111 of the first drive unit 3110 to move in the direction of the rotation axis of the chuck device 3116 (in the horizontal direction in FIG. 26) with respect to the base 3110b. ing. Note that while the rotational torsion test is being performed, the movable plate 3111 is firmly fixed to the base 3110b by a locking mechanism (not shown). Further, the second drive section 3120 also includes a movable plate drive mechanism similar to the first drive section 3110.

The torsion test device 3100 according to the thirteenth embodiment of the present invention described above performs a rotational torsion test on a transmission unit for an FR vehicle, but the present invention is a basic example of the thirteenth embodiment described above. Although not limited to this configuration, apparatuses for performing rotational torsion testing of other power transmission mechanisms are also encompassed by the present invention. The first, second and third variations of the thirteenth embodiment of the present invention described below are torsional tests suitable for testing transmission units for FF vehicles, differential gear units, and transmission units for 4WD vehicles, respectively. This is an example of the configuration of the device.

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

The torsion test apparatus 3200 of this modification includes a first drive section 3210 that drives the input shaft I of the specimen T2, a second drive section 3220 that drives the left output shaft OL, and a third drive section that drives the right output shaft OR. 3230. Further, the torsion test device 3200 includes a control unit C3a that integrally controls its operation. 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. Therefore, a redundant explanation of specific configurations will be omitted.

When performing a rotational torsion test on the specimen T2 using the torsion test apparatus 3200 of this modification, for example, the first drive section 3210 drives the input shaft I at a predetermined rotation speed, and at the same time, the second drive section 3220 and The third drive unit 3230 rotationally drives the left output shaft OL and the right output shaft OR so that a predetermined torque is applied.

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

The transmission unit to be tested using the torsion testing device 3200 of this modification is a device in which an input shaft I, a left output shaft OL, and a right output shaft OR are connected via gears, etc. When testing, 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. Furthermore, 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 understand the behavior of the specimen T2 during the torsion test, it is preferable to be able to individually measure the torques applied to the input shaft I, the left output shaft OL, and the right output shaft OR. In this modification, since torque sensors are provided in all of the first drive section 3210, second drive section 3220, and third drive section 3230, the input shaft I and the left output shaft of the transmission unit (specimen T2) are The torques applied to each of the OL and the right output shaft OR can be measured individually.

Note that the second drive section 3220 and the third drive section 3230 may be controlled so that the torque of the left output shaft OL and the torque of the right output shaft OR draw the same waveform, or they may be different ( For example, a configuration may be adopted in which the first drive section 3210, the second drive section 3220, and the third drive section 3230 are controlled so as to draw waveforms (of opposite phases).

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

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

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 that drives the right output shaft OR. Equipped with 3330. Further, the torsion test device 3300 includes a control unit C3b that integrally controls its operation. The structures of the first drive section 3310, the second drive section 3320, and the third drive section 3330 are 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, so the structures overlap. Description of the specific configuration will be omitted.

When performing a rotational torsion test on the specimen T3 using the torsion test apparatus 3300 of this modification, for example, the input shaft I is driven at a predetermined rotation speed by the first drive part 3310, and at the same time, the second drive part 320 and the third The drive unit 3330 drives the left output shaft OL and the right output shaft OR so that torque is applied to each of them.

By controlling the first drive section 3310, the second drive section 3320, and the third drive section 3330 as described above, variable torque can be applied to each axis of the specimen T3 while rotating each axis of the specimen T3. This allows testing to be conducted under conditions close to actual usage conditions.

Similarly to the transmission unit, the differential gear unit is also a device in which the input shaft I, the left output shaft OL, and the right output shaft OR are connected via gears. The magnitude of the torque applied to the left output shaft OL and the magnitude of the torque applied to the right output shaft OR do not match. Furthermore, the magnitudes of 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 understand the behavior of the specimen T3 during the test, it is desirable to be able to individually measure the torques of the input shaft I, left output shaft OL, and right output shaft OR. In this modification, since torque sensors are provided in all of the first drive section 3310, second drive section 3320, and third drive section 3330, the input shaft I of the differential gear unit (specimen T3) and the left side output The torques applied to each of the shaft OL and the right output shaft OR can be measured individually.

Note that the second drive unit 3320 and the third drive unit 3330 may be configured to 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, Alternatively, the second drive section 3320 and the third drive section 3330 may be controlled so that they draw different waveforms (for example, the speed difference with the input shaft I is in opposite phase).

Alternatively, the left output shaft OL and the right output shaft OR may be driven to rotate at a constant speed, and the input shaft I may be driven such that the speed varies at a constant cycle. Alternatively, the input shaft I, the left output shaft OL, and the right output shaft OR may all be driven so that their rotational speeds vary.

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

The torsion test device 3400 of this modification includes a first drive section 3410 that drives the input shaft I of the specimen T4, a second drive section 3420 that drives the left output shaft OL, and a third drive section that drives the right output shaft OR. 3430 and a fourth drive section 3440 that drives the rear output shaft OP. Furthermore, the torsion test device 3400 includes a control unit C3c that integrally controls its operation. The structures of the first drive section 3410, the second drive section 3420, the third drive section 3430, and the fourth drive section 3440 are all the same as the first drive section 3110 and the second drive section 3120 of the basic example of the thirteenth embodiment. Therefore, a redundant explanation of specific configurations will be omitted.

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

FIG. 31 is a side view of a torsion testing device 4000 according to the fourteenth embodiment of the present invention. The torsion test apparatus 4000 is an apparatus that uses only one two-axis output servo motor 150A to simultaneously perform rotational torsion tests on two specimens T3a and T3b. The torsion test device 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.

FIG. 32 is an enlarged view of the drive section 4200. The drive section 4200 includes a two-axis output servo motor 150A and a pair of drive transmission sections 4200A and 4200B. The two-axis output servo motor 150A is connected to a control unit C4, and its drive is controlled by the control unit C4. The drive transmission units 4200A and 4200B reduce the rotation speed 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 specimens T3a and T3b. Since the drive transmission section 4200A and the drive transmission section 4200B have the same configuration, only one of the drive transmission sections 4200A will be described in detail.

The drive transmission unit 4200A includes a frame 4210, a reduction gear 4220, a pulley 4230, a timing belt 4240, a rotary encoder 4250, and a chuck device 4260. The frame 4210 is an angle (L-shaped member)-shaped frame attached to the fixed base 4100, and includes a bottom plate 4212, which is a flat plate horizontally arranged on the fixed base 4100, and a flat plate standing upright from one end of the upper surface of the bottom plate 4212. A vertical plate 4214 is provided, and a pair of rib plates 4216 are 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 interconnected by welding. The vertical plate 4214 is arranged perpendicularly to the first output shaft 150A2a of the two-axis output servo motor 150A, and has an opening 4214a formed coaxially with the first output shaft 150A2a. A reduction gear 4220 is inserted into the opening 4214a of the vertical plate 4214 and is fixed thereto.

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

A first output shaft 150A2a of the two-axis output servo motor 150A is connected to an input shaft (not shown) of a reduction gear 4220. Furthermore, 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 two-axis output servo motor 150A is decelerated by the reducer 4220, the torque is amplified, and then transmitted to the input shaft of the specimen T3a via the chuck device 4260.

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 making up the reducer 4220 is always completely immersed in the lubricating oil. There is. In torsion tests, the test piece is subjected to a reciprocating torsional load in the normal range, so the angle at which the test piece is twisted is several tens of degrees at most, and even for the input shaft of the reducer, the amplitude of repeated rotation is one rotation (360 degrees). There are many things that cannot be avoided. By filling the internal space of the reducer 4220 with lubricating oil, even in this type of use, the gear mechanism that constitutes the reducer is prevented from running out of oil film, and the heat dissipation effect of the lubricating oil is enhanced, and the tooth surface is Burn-in is effectively prevented.

A pulley 4230 is provided on the outer periphery of the output shaft 4228. Further, a rotary encoder 4250 is arranged on the vertical plate 4214 of the frame 4210 below the speed reducer 4220. A timing belt 4240 is wound around a pulley 4252 attached to the input shaft of the rotary encoder 4250 and a pulley 4230 attached to the output shaft 4228 of the reducer 4220, and the rotation of the output shaft 4228 of the reducer 4220 is as follows: The signal is transmitted to a rotary encoder 4250 via a 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.

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

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) frame attached to the fixed base 4100 with bolts B, and includes a bottom plate part 4412 horizontally arranged on the fixed base 4100, and one end of the upper surface of the bottom plate part 4412 (Fig. A vertical plate 2414 that is a flat plate stands upright from the left end of 31, and a pair of rib plates 2416 that are vertically connected to the bottom plate 4412 and the vertical plate 2414. The bottom plate 4412, the vertical plate 4214, and the rib plate 4216 are interconnected by welding. Further, the bearing portion 4460 is fixed to the bottom plate portion 4412 with bolts B on the side closer to the drive portion 4200 than the vertical plate 2414 and the rib plate 2416.

The fixed base 4100 includes a first reaction force section moving mechanism (not shown) that smoothly moves the first reaction force section 4400A in the direction of the first output shaft 150A2a of the two-axis output servo motor 150A. By operating the first reaction force moving mechanism with the bolt B fixing the upper part to the fixed base 4100 loosened, the first reaction force part 4400A can be smoothly moved in the direction of the first output shaft 150A2a. ing. Note that the fixed base 4100 also includes a second reaction force section moving mechanism (not shown) that smoothly moves the second reaction force section 4400B in the direction of the second output shaft 150A2b of the two-axis output servo motor 150A.

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

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

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

When performing a rotational torsion test using the torsion test apparatus 4000 configured as described above, the input shaft of the specimen T3a is attached to the chuck device 4260 of the drive transmission section 4200A, and the chuck device of the first reaction force section 4400A is mounted as described above. The output shaft of the specimen T3a is attached to 4480. Similarly, the input shaft of the specimen T3b is attached to the chuck device 4260 of the drive transmission section 4200B, and the output shaft of the specimen T3b is attached to the chuck device 4480 of the second reaction force section 4400B. When the two-axis output servo motor 150A is driven in this state, the first output shaft 150A2a and the second output shaft 150A2b rotate in the same phase, and the chuck devices 4260 of the drive transmission section 4200A and the drive transmission section 4200B also rotate in the same phase. . As a result, the same amount of twist is applied to the specimens T3a and T3b, that is, the torsion test under the same conditions is performed on the specimens T3a and T3b.

According to the configuration of the fourteenth embodiment described above, the torsion test (fatigue test) of the two specimens T3a and T3b can be performed simultaneously using one servo motor and control unit C4, so that the torsion test (fatigue test) can be performed efficiently. It becomes possible to conduct tests.

In addition, by providing a linear motion converter such as a feed screw mechanism instead of the drive transmission parts 4200A and 4200B, compressive force and tensile force can be repeatedly applied to the two specimens T3a and T3b (or A tension/compression test device is obtained (which applies compressive force to one side of T3b and tensile force to the other side). With this configuration, it is possible to perform a repeated expansion/contraction test on the two specimens T3a and T3b (or a tensile test on the specimen T3a and a compression test on the specimen T3b) at the same time. Moreover, at this time, by eliminating the first reaction force section 4400A and the second reaction force section 4400B, it becomes possible to perform the vibration test on the two specimens T3a and T3b at the same time.

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

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

FIG. 38 is a block diagram of a control system for a vibration testing device according to an embodiment of the invention. The first, second, and third actuators 5200, 5300, and 5400 are provided with vibration sensors 5220, 5320, and 5420, respectively. Based on the outputs of these vibration sensors, the control unit C5 feedback-controls the first, second, and third actuators 5200, 5300, and 5400 (specifically, the servo motor units 150X, 150Y, and 150Z), thereby achieving the desired The table 5100 and the workpiece mounted thereon can be excited with an amplitude and frequency of (these parameters are typically set as a function of time). Servo motor units 150X, 150Y, and 150Z are the same as servo motor unit 150 of the first embodiment.

The first, second, and third actuators 5200, 5300, and 5400 have a configuration in which a motor, a power transmission member, and the like are mounted on base plates 5202, 5302, and 5402, respectively. The base plates 5202, 5302, 5402 are fixed onto the device base 5002 by bolts (not shown).

Furthermore, adjusters A are arranged on the device base 5002 at a plurality of positions close to the base plates 5202, 5302, and 5402. The adjuster A has a female threaded portion A1 fixed to the device base 5002 with a bolt AB, and a male threaded portion A2 screwed into the female threaded portion A1. The male thread part A2 is a cylindrical member with a thread formed on its cylindrical surface, and by engaging the male thread part A2 with a screw hole formed in the female thread part A1 and rotating it, the male thread part A2 can be rotated. The portion A2 can be moved forward and backward relative to the corresponding base plate. One end of the male threaded portion A2 (the side that is proximal to the corresponding base plate) is formed into a substantially spherical shape, and by bringing this protrusion into contact with the side surface of the corresponding base plate, the base plate You can make fine adjustments to the position. Further, a hexagonal hole for a hexagonal wrench (not shown) is formed at the other end of the male threaded portion A2 (the side distal to the corresponding base plate). In addition, once the base plates 5202, 5302, and 5402 are fixed, a nut A3 is attached to the male thread part A2 to prevent the male thread part A2 from loosening due to vibrations that may be transmitted from the base plate to the adjuster A in a vibration test. There is. The nut A3 is attached so that its one end surface is in contact with the female threaded part A1, and from this state, the nut A3 is screwed in and the female threaded part A1 is pushed in to apply an axial force to the male threaded part A2 and the female threaded part A1. The frictional force generated between the threads of the male threaded portion A2 and female threaded portion A1 due to this axial force prevents the female threaded portion A1 from loosening from the male threaded portion A2.

Next, the configuration of the first actuator 5200 will be explained. FIG. 34 is a side view of the first actuator 5200 according to the embodiment of the present invention viewed from the Y-axis direction (from the right side to the left side in FIG. 33). This side view is partially cut away to show the internal structure. Further, 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 will be referred to as the "X-axis positive direction", and the direction along the X-axis from the table 5100 to the first actuator will be referred to as the "X-axis". "in the negative direction".

As shown in FIG. 34, a frame 5222 consisting of a plurality of beams 5222a welded to each other and a top plate 5222b is fixed on the base plate 5202 by welding. Further, the bottom plate 5242 of the support mechanism 5240 for supporting the drive mechanism 5210 for vibrating the table 5100 (FIG. 33) and the coupling mechanism 5230 for transmitting the excitation movement by the drive mechanism 5210 to the table 5100 is attached to the frame. It is fixed onto the top plate 5222b of 5222 via bolts (not shown).

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 connects the drive shaft 152X of the servo motor unit 150X and the ball screw 5218. Further, the bearing portion 5216 is supported by a bearing support plate 5244 vertically fixed to the bottom plate 5242 of the support mechanism 5240 by welding, and rotatably supports the ball screw 5218. The ball nut 5219 engages with the ball screw 5218 while being supported by the bearing support plate 5244 so as not to move around its axis. Therefore, when the servo motor unit 150X is driven, the ball screw rotates and the ball nut 5219 advances and retreats in its axial direction (ie, the X-axis direction). This movement of ball nut 5219 is transmitted to table 5100 via coupling mechanism 5230, thereby driving table 5100 in the X-axis direction. By controlling the servo motor unit 150X to switch the rotational direction of the servo motor unit 150X in short cycles, the table 5100 can be vibrated in the X-axis direction with a desired amplitude and cycle.

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

Note that since the servo motor unit 150X is cantilevered by the motor support plate 5246, 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.

The bearing portion 5216 includes a pair of angular ball bearings 5216a and 5216b assembled face-to-face (5216a is located on the negative side of the X-axis, and 5216b is located on the positive side of the X-axis). are doing. The angular ball bearings 5216a and 5216b are housed in the hollow portion of the bearing support plate 5244. A bearing pressing plate 5216c is provided on one surface of the angular ball bearing 5216b (the surface on the X-axis positive direction side), and by fixing this bearing pressing plate 5216c to the bearing support plate 5244 using bolts 5216d, The angular ball bearing 5216b is pushed in the negative direction of the X-axis. Further, in the ball screw 5218, a threaded portion 5218a is formed on the cylindrical surface adjacent to the bearing portion 5216 on the negative side of the X-axis. A collar 5217 having a female thread formed on the inner periphery is attached to this threaded portion 5218. By rotating the collar 5217 with respect to the ball screw 5218 and moving it in the positive direction of the X-axis, the angular ball bearing 5216a is pushed in the positive direction of the X-axis. In this way, since the angular ball bearings 5216a and 5216b are pushed in toward each other, they come into close contact with each other and a suitable preload is applied to the bearings 5216a and 5216b.

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

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

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

A pair of X-axis rails 5237 are rails that both extend in the X-axis direction, and are fixed on the bottom plate 5242 of the support mechanism 5240 in parallel 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 attachment 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 attachment member 5238. In this way, the nut guide 5232 is guided by the X-axis rail 5237 via the runner block attachment member 5238 and the X-axis runner block 5233, and is thereby movable only in the X-axis direction.

As described above, since the movement direction of the nut guide 5232 is limited only to the X-axis direction, when the servo motor unit 150X is driven to rotate the ball screw 5218, the nut guide 5232 and the nut guide 5232 are engaged with each other. The table 5100 moves forward and backward in the X-axis direction.

A position detection means 5250 is disposed on one side surface 5238a of the runner block mounting member 5238 in the Y-axis direction (the front side in FIG. 34, the right side in FIG. 35). The position detection means 5250 includes three proximity sensors 5251 arranged at regular intervals in the X-axis direction, a detection plate 5252 provided on the side surface 5238a of the runner block mounting member 5238, and a sensor support plate 5253 that supports the proximity sensors 5251. have. Proximity sensors 5251 are elements that can detect whether some object is close (for example, within 1 millimeter) in front of each proximity sensor. Since the side surface 5238a of the runner block attachment member 5238 and the proximity sensor 5251 are sufficiently apart, the proximity sensor 5251 can detect whether the detection plate 5252 is present in front of each proximity sensor 5251. The control unit C5 of the vibration testing apparatus 5000 can feedback-control the servo motor unit 150X using, for example, the detection result of the proximity sensor 5251 (FIG. 38).

Further, on the bottom plate 5242 of the support mechanism 5240, regulation blocks 5236 are provided so as to sandwich the X-axis runner block 5233 from both sides in the X-axis direction. This restriction block 5236 is for restricting the movement range of the nut guide 5232. That is, if the servo motor unit 150X is driven to continue moving the nut guide 5232 in the positive direction of the X-axis, the regulation block 5236 and the runner block mounting member disposed in the positive direction of the X-axis will eventually 5238, and the nut guide 5232 can no longer move in the positive direction of the X-axis. The same applies when the nut guide 5232 continues to move in the negative direction of the X-axis, and the regulation block 5236 placed on the negative side of the X-axis comes into contact with the runner block mounting member 5238, causing the nut guide to move further 5232 cannot move in the negative direction of the X-axis.

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

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 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. Moreover, 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 side to the right side in FIG. 33). Also in FIG. 37, a portion is 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 referred to as the positive Y-axis direction, and the direction along the Y-axis from the table 5100 to the second actuator 5300 is referred to as the negative Y-axis. Define direction.

As shown in FIGS. 36 and 37, a frame 5422 is provided on the base plate 5402 and includes 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. It is being Each beam 5422a has a lower end welded to the upper surface of the base plate 5402 and an upper end welded to the lower surface of the top plate 5422b, respectively. Further, a bearing support plate 5442 of the support mechanism 5440 is fixed onto the top plate 5422b of the frame 5422 via bolts (not shown). This bearing support plate 5442 is a member for supporting the drive mechanism 5410 for vertically vibrating the table 5100 (FIG. 33) and the coupling mechanism 5430 for transmitting the vibration motion by the drive mechanism 5410 to the table. It is.

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. Coupling 5460 connects drive shaft 152Z of servo motor unit 150Z and ball screw 5418. Further, the bearing portion 5416 is fixed to the aforementioned bearing support plate 5442, and rotatably supports the ball screw 5418. The ball nut 5419 engages with the ball screw 5418 while being supported by a 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 (that is, the Z-axis direction). This movement of ball nut 5419 is transmitted to table 5100 via coupling mechanism 5430, thereby driving table 5100 in the Z-axis direction. By controlling the servo motor unit 150Z to switch the rotational direction of the servo motor unit 150Z in short cycles, the table 5100 can be vibrated in the Z-axis direction (vertical direction) with a desired amplitude and cycle.

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

Note that 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 located at a position lower than the base plate 5402. will be placed in For this reason, the device base 5002 is provided with a cavity 5002a for housing the servo motor unit 150Z. Furthermore, the base plate 5402 is provided with an opening 5402a through which the servo motor unit 150Z passes.

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

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

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

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

Furthermore, in this embodiment, since the movable frame 5432 supports the relatively heavy table 5100 and workpiece, the distance between the X-axis rail 5434 and the Y-axis rail 5435 is set to the distance between the Y-axis rail 5234 and the Z-axis rail 5234 of the first actuator 5200. It is wider than the shaft rail 5235. For this reason, if the table 5100 and the movable frame 5432 are connected by only one intermediate stage like the first actuator 5200, the intermediate stage will become larger and the load applied to the movable frame 5432 will increase. Therefore, 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, so that the magnitude of the load applied to the movable frame 5432 is minimized. I'm suppressing it.

The two pairs of Z-axis rails 5437 are rails extending in the Z-axis direction, and are fixed to each side wall 5432c of the movable frame 5432 in pairs in parallel 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 attachment 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. It has become. Further, in this embodiment, when a particularly heavy workpiece with a high center of gravity is fixed on the table 5100, a large moment around the X-axis and/or the Y-axis is likely to be applied to the movable frame 5432. Therefore, the runner block mounting member 5438 is reinforced with ribs to withstand this rotational moment. Specifically, a pair of first ribs 5438c are provided at the corners formed by the side plate 5438a and the bottom plate 5438b at both ends in the Y-axis direction of the runner block mounting member 5438, and furthermore, a pair of first ribs 5438c are provided between the pair of first ribs 5438c. A second rib 5438d is provided.

In this way, the Z-axis runner block 5433 is fixed to the frame 5422 and is slidable on the Z-axis rail 5437. Therefore, the movable frame 5432 is slidable in the vertical direction, and movement of the movable frame 5432 in directions other than the vertical direction is restricted. As described above, since the moving direction of the movable frame 5432 is limited only to the vertical direction, when the servo motor unit 150Z is driven to rotate the ball screw 5418, the movable frame 5432 engages with the movable frame 5432. The table 5100 moves forward and backward in the vertical direction.

Furthermore, the third actuator 5400 is also provided with a position detecting means (not shown) similar to the position detecting 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 the position detection means (FIG. 38).

As explained above, in this embodiment, two pairs of rails and an intermediate stage configured to be slidable with respect to the rails are provided between each actuator whose drive shafts are perpendicular to each other and the table 5100. There is. This allows the table 5100 to slide in any direction on a plane perpendicular to the driving direction of the actuator for each actuator. Therefore, even if the table 5100 is displaced by a certain actuator, the load or moment due to this displacement will not be applied to the other actuators, and the other actuators and the table 5100 will engage with each other via the intermediate stage. is maintained. That is, even if the table is displaced to an arbitrary position, a state in which each actuator can displace the table is maintained. Therefore, in this embodiment, it is possible to simultaneously drive the three actuators 5200, 5300, and 5400 to vibrate the table 5100 and the workpiece fixed thereon in three axial directions.

In this embodiment, as described above, a connecting portion is provided between the actuators 5200, 5300, 5400 and the table 5100, and includes a guide mechanism that combines a rail and a runner block. Similar guide mechanisms are also provided on actuators 5200, 5300, and 5400, and are used to guide the nuts of the ball screw mechanisms of each actuator.

Further, in each of the embodiments described above, 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 (for example, an inverter motor) whose rotor has a small moment of inertia and can be driven at high acceleration or jerk. In this case, similarly to each of the above embodiments, a configuration may be adopted in which an encoder is provided on the electric motor and feedback control is performed based on the rotational state (for example, rotation speed and angular position) of the output shaft of the electric motor detected by the encoder.

Further, although the above embodiment is an example in which the present invention is mainly applied to a durability testing device for a power transmission device for an automobile, the present invention is not limited thereto, and can be used in various applications in general industry. I can do it. For example, the present invention can be used to evaluate the mechanical properties and durability of two-wheeled vehicles, agricultural machinery, construction machinery, railway vehicles, ships, aircraft, power generation systems, water supply and drainage systems, or the various parts that constitute these. can.

The above is the description of the present embodiment, but the present invention is not limited to the above configuration, and various modifications can be made within the scope of the technical idea of the present invention. For example, in each of the above embodiments, the servo motor unit 150 (or the torque applying servo motor unit 132 ) is used, however, a servo motor unit in which one servo motor 150B and a plurality of two-axis output servo motors 150A are connected in three or more stages may also be used.

<Addendum>
In order to further expand the scope of application of servo motor type test equipment, there is a need for even higher output while maintaining the high acceleration characteristics of ultra-low inertia servo motors.

In addition, since the cost of the servo motor accounts for a large proportion of the manufacturing cost of the servo motor type test equipment, there is a need for a servo motor type test equipment that can test multiple specimens at the same time using one servo motor. There is.

However, simply increasing the output of the 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. Additionally, this increases the output ratio of the servo motor's moment of inertia (the ratio of the moment of inertia to the servo motor's output), which reduces acceleration characteristics (including jerk) and limits the frequency range of variable loads that can be output. A problem arises in that the value decreases.

In addition, since conventional servo motors have only one output shaft, in order to test multiple specimens at the same time, it is necessary to install a gear mechanism to distribute the power, which increases frictional resistance and There was a problem of increasing the size of the device.

According to an embodiment of the present invention, a cylindrical main body frame, a substantially flat first bracket attached to one axial end of the main body frame, and a substantially flat first bracket attached to the other axial end of the main body frame. a flat second bracket; a drive shaft that passes through the hollow part of the main body frame, penetrates the first bracket and the second bracket, and is rotatably supported by bearings provided in the first bracket and the second bracket, respectively; , one end of the drive shaft protrudes outward from the first bracket to serve as a first output shaft that outputs driving force to the outside, and the other end protrudes outward from the second bracket to serve as a second output shaft. A two-axis output servo motor is provided.

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

The first bracket and the second bracket may have a second mounting surface perpendicular to the first mounting surface, which is provided with a tapped hole for mounting a two-axis output servo motor.

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

According to an embodiment of the present invention, a cylindrical main body frame, a load side bracket attached to one axial end of the main body frame, and an anti-load side bracket attached to the other axial end of the main body frame. , a drive shaft that passes through the hollow part of the main body frame, penetrates the first bracket and the second bracket, and is rotatably supported by bearings provided on the load side bracket and the anti-load side bracket, respectively, the drive shaft A second servo motor with only one end protruding outward from the load side bracket and forming an output shaft that outputs driving force to the outside, the above-mentioned two-axis output servo motor, the load side bracket and the second bracket. A connecting member that connects each other at a predetermined interval, a coupling that connects the output shaft of the second servo motor, and the second output shaft of the two-axis output servo motor, and the second servo motor and the two-axis output servo motor. A servo motor unit is provided, including a drive control section that drives the servo motors in the same phase.

The above servo motor unit is equipped with the above two-axis output servo motor, and a rotary encoder that detects the rotational position of the drive shaft is 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 the signal output by the rotary encoder.

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

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

The rotational torsion test device includes a drive power supply section that supplies drive power to the servo motor unit, and a drive power transmission path that transmits drive power from the drive power supply section to the servo motor unit, which are arranged outside the load application section. , a torque signal processing section disposed outside the load application section that processes the torque signal output by the torque sensor, and a torque signal transmission line that transmits the torque signal from the torque sensor to the torque signal processing section. The power transmission path includes an external drive power transmission path arranged outside the load application section, an internal drive power transmission path arranged inside the load application section and rotates together with the load application section, and an external drive power transmission path and the internal drive power transmission path. a first slip ring section that connects the drive power transmission path, and the torque signal transmission path is wired inside the load application section and the external torque signal transmission path arranged outside the load application section, an internal torque signal transmission path that rotates together with the applying section; and a second slip ring section that connects the external torque signal transmission path and the internal torque signal transmission path, the second slip ring section being separated from the first slip ring section. It is also possible to have a configuration in which they are arranged as follows.

The rotation drive unit includes a second motor and a drive force transmission unit that transmits the drive force of the second motor to the load application unit and the second drive shaft to rotate them in the same phase, and the drive force transmission unit includes a second motor The present invention may include a first driving force transmitting section that transmits the driving force of the second motor to the second drive shaft, and a second driving force transmitting section that transmits the driving force of the second motor to the load applying section.

The first driving force transmitting section and the second driving force transmitting section each include an endless belt mechanism, and the first driving force transmitting section has a third driving shaft driven by a second motor arranged parallel to the rotation axis. , a first drive pulley coaxially fixed to the third drive shaft, a first driven pulley coaxially fixed to the load applying section, and a first drive pulley spanned between the first drive pulley and the first driven pulley. an endless belt, the second drive force transmission section includes a fourth drive shaft coaxially connected to the third drive shaft, a second drive pulley fixed to the fourth drive shaft, and a second drive shaft connected to the first drive shaft. The present invention may include a second driven pulley that is fixed, and a second endless belt that is stretched around the second driving pulley and the second driven pulley.

According to an embodiment of the present invention, there is provided a torsion test device that applies a torque to an input/output shaft of a specimen, which is a power transmission device, including a first driving portion connected to the input shaft of the specimen, and a first driving portion connected to the input shaft of the specimen. a second drive section connected to the output shaft, and the first drive section and the second drive section include the above-mentioned servo motor unit, a reducer that decelerates the rotation of the drive shaft of the servo motor unit, and a speed reducer that reduces the rotation of the drive shaft of the servo motor unit. A chuck to which an input shaft or an output shaft is attached and transmits the output of the reducer to the input shaft or output shaft of the specimen, and a torque sensor that transmits the output of the reducer to the chuck and detects the torque output by the reducer. and a tachometer for detecting the number of rotations of the chuck.

The reducer includes a spindle that connects the torque sensor and the chuck, and a bearing that rotatably supports the spindle, and the reducer includes a gear case, a bearing, and a gear mechanism supported by the gear case via the bearing. The gear mechanism of the reducer that transmits the driving force of the servo motor to the specimen, the torque sensor, and the load of the power transmission shaft including the spindle may be supported by the spindle and the gear mechanism of the reducer.

According to an embodiment of the present invention, there is provided a torsion test apparatus that simultaneously tests a first specimen and a second specimen, the above two-axis output servo motor and the rotation of the first output shaft being controlled by the first specimen. A first drive transmission section that transmits the rotation to one end of the specimen, a first reaction force section that fixes the other end of the first specimen, and a first drive transmission section that transmits the rotation of the second output shaft to the one end of the second specimen. The first drive transmission section and the second drive transmission section each include a second drive transmission section and a second reaction force section that fixes the other end of the second specimen. The first reaction force section and the second reaction force section each include a chuck device for attaching the other end of the first specimen or the second specimen. It may also be configured to include a torque sensor that detects the torque applied to the specimen.

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

According to an embodiment of the present invention, a frame, the above-mentioned servo motor unit fixed to the frame, a servo motor, a deceleration mechanism that decelerates the rotation of the servo motor, and an input shaft of the deceleration mechanism and an input shaft of the servo motor are provided. a coupling that connects the drive shaft; a first grip that is fixed to the output shaft of the speed reduction mechanism and grips one end of the specimen; and a second grip that is fixed to the frame and grips the other end of the specimen. A torsion testing device is provided, comprising:

According to an embodiment of the present invention, the above servo motor unit, a feed screw, a coupling that connects the feed screw and the drive shaft of the servo motor unit, a nut that engages with the feed screw, and movement of the nut. A linear actuator is provided that includes a linear guide whose direction is limited only to the axial direction of a feed screw, and a support plate to which a servo motor and a linear guide are fixed.

According to an embodiment of the present invention, the table includes a table for attaching a workpiece, and a first actuator capable of vibrating the table in a first direction, and the first actuator includes the above-mentioned servo motor unit and a servo motor unit. A vibration excitation device is provided that includes a ball screw mechanism that converts rotational motion of a motor unit into translational motion in a first direction or a second direction.

According to an embodiment of the present invention, a table for mounting a workpiece, a first actuator capable of vibrating the table in a first direction, and a first actuator capable of vibrating the table in a second direction orthogonal to the first direction are provided. a second actuator capable of swinging; a first coupling means slidably coupling the table in a second direction relative to the first actuator; and a first coupling means slidably coupling the table in a first direction relative to the second actuator. a second connecting means, wherein the first actuator and the second actuator include the above-mentioned servo motor unit and a ball screw mechanism that converts rotational movement of the servo motor unit into translational movement in the first direction or the second direction. A vibrating device is provided which includes the following.

According to an embodiment of the present invention, a table for mounting a workpiece, a first actuator capable of vibrating the table in a first direction, and a first actuator capable of vibrating the table in a second direction orthogonal to the first direction are provided. a second actuator capable of vibrating the table; 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 slidably connecting the table to the second actuator in the first direction and the third direction; a second connecting means slidably connecting the table to the second actuator in the first direction and the third direction; a third connecting means slidably connected to the three actuators in the first direction and the second direction, and the first actuator, the second actuator, and the third actuator are connected to the servo motor unit and the servo motor unit. A vibration excitation device is provided, each comprising a ball screw mechanism that converts rotational motion of a motor unit into translational motion in a first direction, a second direction, or a third direction.

According to one embodiment of the present invention, the first servo motor, the cylindrical casing, the second servo motor fixed in the casing, and the frame fixed in the casing and the output shaft of the servo motor are connected. A torque applying unit having a reducer including an input shaft and a reducer that decelerates and outputs the rotation of the input shaft and protrudes from a casing, and a test object is attached and one end is connected to the output shaft of the reducer. A first shaft, a second shaft whose one end is connected to the output shaft of the motor, and a connection part to which the output shaft of the reducer and the casing of the torque applying unit are connected, and the rotary movement of the output shaft and the casing is connected to the gear. a first gear box that transmits rotational motion of the first shaft and the second shaft, and a connecting portion to which the other end of the first shaft and the other end of the second shaft are connected, and transmits the rotational motion of the first shaft and the second shaft using gears; A torsion testing device is provided having a second gearbox that has a second gearbox that has a second gearbox that has a second gearbox that has a second gearbox that has a second gearbox that has a second gearbox that has a second gearbox that has a second gearbox that has a second gearbox that has a second gearbox that has a second gearbox that has a second gearbox that has a second gearbox that has a second gearbox that has a second gearbox that has a second gearbox that has a second gearbox that has a second gearbox that has a second gearbox;

According to the present invention, since power is circulated through the first gearbox and the second gearbox, there is less power loss compared to the conventional configuration in which power is circulated using a belt mechanism, and the power is circulated through the first and second gearboxes. A lower cost torsion testing device is realized.

According to an embodiment of the present invention, an output shaft, a control unit that controls rotation of the output shaft to generate simulated power that simulates predetermined power, and a torque instructed by the control unit that applies to the output shaft , a rotatably supported load applying section, and a rotary drive section that rotationally drives the load applying section at a rotational speed instructed by a control section, and the load applying section has a rotating shaft connected to an output shaft. A power simulator is provided that includes a servo motor.

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

By using both ends of the drive shaft as the first output shaft and the second output shaft, it is possible to distribute the output without adding a power distribution means such as a gear mechanism, and the friction caused by the addition of the power distribution means can be reduced. This prevents an increase in resistance and an increase in the size of the test equipment. In addition, this configuration makes it possible to combine the output by connecting one of the first output shaft and the second output shaft to the output shaft of another servo motor, which reduces the size of the servo motor and the resulting moment of inertia. It becomes possible to achieve high output while suppressing deterioration in acceleration characteristics due to an increase in .

Claims (11)

a rotatably supported casing;
an inverter motor capable of rotationally driving the casing;
an electric motor attached to the casing;
Equipped with
The electric motor has a rated output of 10 kW or more and a moment of inertia of the rotating part of 10 ⁻² kg・m ² or less,
adding rotation generated by the electric motor to the rotation input to the casing and outputting the resultant;
Load applying section. a connecting shaft rotationally driven by the electric motor;
a bearing portion rotatably supporting the casing;
The casing has a cylindrical shaft part rotatably supported by the bearing part,
A bearing is provided on the inner periphery of the shaft portion to rotatably support the connecting shaft passed through the hollow portion of the shaft portion.
The load applying section according to claim 1. the casing is cylindrical;
the electric motor is disposed within a hollow part of the casing;
The load applying section according to claim 1 or 2. a shaft of the electric motor is arranged concentrically with a rotation shaft of the casing;
The load applying section according to any one of claims 1 to 3. the electric motor includes a motor case;
the motor case is fixed to the casing via a plurality of fixing rods;
The load applying section according to any one of claims 1 to 4. The motor case includes a bracket provided with a second bearing that rotatably supports the shaft of the electric motor,
one end of the fixed rod is fixed to the bracket;
The load applying section according to claim 5. The casing includes a cylindrical body that houses the electric motor,
the other end of the fixed rod is fixed to the trunk;
The load applying section according to claim 6. comprising a speed reducer that reduces the rotation of the electric motor,
The speed reducer is
Equipped with a mounting flange,
fixed to the casing by sandwiching and tightening the mounting flange between the body and the shaft;
The load applying part according to claim 7, which refers directly or indirectly to claim 2. 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 line is
an external power transmission line disposed outside the casing;
an internal power transmission line disposed inside the casing and rotatable together with the casing;
a slip ring unit connecting the external power transmission path and the internal power transmission path;
The load applying section according to any one of claims 1 to 8. Equipped with the load applying section according to any one of claims 1 to 9,
Mechanical testing equipment. A load applying section according to any one of claims 1 to 9,
a first workpiece attachment portion to which one end of the specimen is attached;
a second workpiece attachment portion to which the other end of the specimen is attached;
Equipped with
Mechanical testing equipment.

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