WO2014058051A1 - Moteur à deux arbres secondaires, unité moteur, simulateur d'alimentation, dispositif de test de torsion, dispositif de test de torsion de rotation, dispositif de test de pneu, actionneur linéaire et dispositif à vibrations - Google Patents

Moteur à deux arbres secondaires, unité moteur, simulateur d'alimentation, dispositif de test de torsion, dispositif de test de torsion de rotation, dispositif de test de pneu, actionneur linéaire et dispositif à vibrations Download PDF

Info

Publication number
WO2014058051A1
WO2014058051A1 PCT/JP2013/077747 JP2013077747W WO2014058051A1 WO 2014058051 A1 WO2014058051 A1 WO 2014058051A1 JP 2013077747 W JP2013077747 W JP 2013077747W WO 2014058051 A1 WO2014058051 A1 WO 2014058051A1
Authority
WO
WIPO (PCT)
Prior art keywords
shaft
unit
servo motor
drive
output
Prior art date
Application number
PCT/JP2013/077747
Other languages
English (en)
Japanese (ja)
Inventor
繁 松本
博至 宮下
一宏 村内
正伸 長谷川
友隆 坂上
Original Assignee
国際計測器株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 国際計測器株式会社 filed Critical 国際計測器株式会社
Priority to CN201380053483.5A priority Critical patent/CN104737423B/zh
Priority to CN201810402131.0A priority patent/CN108663147B/zh
Priority to KR1020207008237A priority patent/KR102190139B1/ko
Priority to JP2014540905A priority patent/JP5986640B2/ja
Priority to KR1020187019525A priority patent/KR102079593B1/ko
Priority to KR1020207008240A priority patent/KR102190153B1/ko
Priority to KR1020157012083A priority patent/KR102093861B1/ko
Publication of WO2014058051A1 publication Critical patent/WO2014058051A1/fr

Links

Images

Classifications

    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K5/00—Casings; Enclosures; Supports
    • H02K5/04—Casings or enclosures characterised by the shape, form or construction thereof
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M13/00—Testing of machine parts
    • G01M13/02—Gearings; Transmission mechanisms
    • G01M13/021—Gearings
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M15/00—Testing of engines
    • G01M15/02—Details or accessories of testing apparatus
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K16/00—Machines with more than one rotor or stator
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K7/00—Arrangements for handling mechanical energy structurally associated with dynamo-electric machines, e.g. structural association with mechanical driving motors or auxiliary dynamo-electric machines
    • H02K7/10—Structural association with clutches, brakes, gears, pulleys or mechanical starters

Definitions

  • the present invention relates to a motor unit in which a plurality of motors including a two-axis output motor and a two-axis output motor are connected in series, a torsion test apparatus, a rotary torsion test apparatus, a tire test apparatus, and a linear motion actuator having a two-axis output servo motor And an excitation device.
  • the present inventors have adopted an ultra-low inertia servo motor in which inertia is significantly reduced compared to a conventional servo motor, and can apply a repeated load of a high frequency of several tens to several hundreds Hz.
  • Various types of fatigue testing devices and vibration testing devices have been put into practical use (for example, Patent Document 1).
  • the above-mentioned servo motor type test apparatus has many serious problems (e.g., installation of large-scale hydraulic supply equipment such as oil tanks and hydraulic pipes, etc.)
  • the scope of application is expanding rapidly because it is necessary to replace the hydraulic oil and solve the work environment and soil contamination caused by the leakage of hydraulic oil.
  • a servo motor type test apparatus capable of simultaneously testing a plurality of specimens using a single servo motor is required. Yes.
  • a cylindrical main body frame a substantially flat plate-like first bracket attached to one axial end of the main body frame, and a substantially flat attached to the other axial end of the main body frame.
  • a flat plate-like second bracket a drive shaft that passes through the hollow portion of the main body frame, passes through the first bracket and the second bracket, and is rotatably supported by bearings provided on the first bracket and the second bracket, respectively.
  • One end of the drive shaft is projected from the first bracket to the outside to form a first output shaft that outputs driving force to the outside, and the other end is projected from the second bracket to the outside to output the second output.
  • a two-axis output servomotor characterized by being configured as a shaft is provided.
  • the first bracket and the second bracket may be formed with a first mounting surface provided with a tapped hole for mounting the biaxial output servomotor on the opposite side of the surfaces facing each other.
  • the first bracket and the second bracket may be provided with a second mounting surface that is provided with a tapped hole for mounting the biaxial output servomotor and is perpendicular to the first mounting surface.
  • the rotary encoder that detects the rotational position of the drive shaft may be provided on at least one of the first bracket and the second bracket.
  • a tubular main body frame a load side bracket attached to one axial end of the main body frame, an anti-load side bracket attached to the other axial end of the main body frame,
  • a drive shaft that passes through the hollow portion of the main body frame, passes through 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,
  • a second servo motor that constitutes an output shaft that projects the driving force to the outside by projecting only one end of the load side bracket, the two-axis output servo motor, the load side bracket, and the second bracket.
  • a coupling member that couples at a predetermined interval, a coupling that couples the output shaft of the second servo motor, and a second output shaft of the two-axis output servo motor;
  • a drive control unit for driving Bomota and the 2-axis output servo motor in the same phase, the servo motor unit comprising a are provided.
  • the servo motor unit includes the biaxial output servo motor described above, and a rotary encoder that detects the rotational position of the drive shaft is attached to one of the load side bracket and the anti-load side bracket. May be configured to control driving of the second servo motor and the two-axis output servo motor based on a signal output from the rotary encoder.
  • the servo motor unit includes the two-axis output servo motor, and the drive control unit is configured to control driving of the second servo motor and the two-axis output servo motor based on a signal output from one of the rotary encoders. May be.
  • a first drive shaft that is attached to one end of a work and rotates about a predetermined rotation axis
  • a first drive shaft that is attached to the other end of the work and rotates about a rotation axis
  • Two driving shafts a load applying portion that supports the first driving shaft and rotationally drives the first driving shaft to apply a torsional load to the workpiece, and at least one that supports the load applying portion rotatably about the rotating shaft
  • the work is rotated through the shaft, and a load is applied to the work by applying a phase difference to the rotation of the first drive shaft and the second drive shaft by the load application unit.
  • a rotational torsion test apparatus is provided that is configured to detect a torsional load, and the load applying unit includes the servo motor unit described above.
  • a rotational torsion test device is disposed outside the load applying unit, and a driving power supply unit that supplies driving power to the servo motor unit, and a driving power transmission path that transmits the driving power from the driving power supply unit to the servo motor unit,
  • a torque signal processing unit that is disposed outside the load applying unit and processes a torque signal output from the torque sensor; and a torque signal transmission path that transmits the torque signal from the torque sensor to the torque signal processing unit.
  • 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 rotating together with the load application section, an external drive power transmission path and the internal A first slip ring portion that connects the drive power transmission path, the torque signal transmission path being disposed outside the load application section, and a load application And an internal torque signal transmission path that rotates together with the load application section, and a second slip ring section that connects the external torque signal transmission path and the internal torque signal transmission path. It is good also as a structure arrange
  • the rotation driving unit includes a second motor and a driving force transmission unit that transmits the driving force of the second motor to the load applying unit and the second driving shaft to rotate in the same phase, and the driving force transmission unit includes the second motor. It is good also as a structure provided with the 1st driving force transmission part which transmits this driving force to a 2nd drive shaft, and the 2nd driving force transmission part which transmits the driving force of a 2nd motor to a load provision part.
  • the first driving force transmission unit and the second driving force transmission unit each include an endless belt mechanism, and the first driving force transmission unit is disposed in parallel with the rotation shaft, and is driven by a second motor.
  • An endless belt, and a second driving force transmission portion coaxially connected to the third driving shaft, a second driving pulley fixed to the fourth driving shaft, and a first driving shaft It is good also as a structure provided with the 2nd endless belt hung around the 2nd driven pulley fixed and the 2nd drive pulley and the 2nd driven pulley.
  • a torsion test device that applies torque to an input / output shaft of a specimen that is a power transmission device, the first drive unit connected to the input shaft of the specimen, A second drive unit connected to the output shaft, wherein the first drive unit and the second drive unit are the servo motor unit, a speed reducer that decelerates the rotation of the drive shaft of the servo motor unit, and a specimen A chuck to which an input shaft or an output shaft is attached and transmits the output of the speed reducer to the input shaft or output shaft of the specimen, and a torque sensor that transmits the output of the speed reducer to the chuck and detects the torque output from the speed reducer
  • a torsion test device including a tachometer for detecting the number of rotations of the chuck.
  • a spindle that connects the torque sensor and the chuck, and a bearing that rotatably supports the spindle.
  • the reduction device includes a gear case, a bearing, and a gear mechanism that is supported by the gear case via the bearing. It is good also as a structure with which the load of the power transmission shaft containing the gear mechanism of a reduction gear which transmits the drive force of a servomotor to a test body, a torque sensor, and a spindle is supported in the gear mechanism of a spindle and a reduction gear.
  • a torsion test apparatus for simultaneously testing a first specimen and a second specimen, wherein the rotation of the two-axis output servo motor and the first output shaft is performed in the first specimen.
  • a first drive transmission portion for transmitting to one end portion of the specimen, a first reaction force portion for fixing the other end portion of the first specimen, and a first transmission portion for transmitting the rotation of the second output shaft to one end portion of the second specimen.
  • 2 drive transmission part, and the 2nd reaction force part which fixes the other end part of the 2nd specimen, the 1st drive transmission part and the 2nd drive transmission part are the 1st specimen or the 2nd specimen.
  • a chuck device for attaching one end portion is provided, and the first reaction force portion and the second reaction force portion are provided with a chuck device for attaching the other end portion of the first specimen or the second specimen, and the first specimen or the second specimen. It is good also as a structure provided with the torque sensor which detects the torque added to the test body.
  • the first drive transmission unit and the second drive transmission unit include a reduction gear that decelerates rotation of the first output shaft or the second output shaft, and a rotary encoder that detects rotation of the output shaft of the reduction gear. Also good.
  • a frame the servo motor unit fixed to the frame, the servo motor, a speed reduction mechanism for reducing the rotation of the servo motor, an input shaft of the speed reduction mechanism, and the servo motor
  • a torsional testing device comprising:
  • the servo motor unit the feed screw, the coupling that connects the feed screw and the drive shaft of the servo motor unit, the nut that engages the feed screw, and the movement of the nut
  • a linear motion actuator is provided that includes a linear guide that limits the direction only to the axial direction of the feed screw, and a support plate to which the servomotor and the linear guide are fixed.
  • a table for mounting a work and a first actuator capable of vibrating the table in a first direction are provided.
  • the first actuator includes the servo motor unit described above and a servo.
  • a vibration device comprising a ball screw mechanism that converts a rotational motion of a motor unit into a translational motion in a first direction or a second direction.
  • a table for mounting a workpiece, a first actuator capable of vibrating the table in a first direction, and a table are applied in a second direction orthogonal to the first direction.
  • a first screw and a second actuator, wherein the first actuator and the second actuator convert the rotational motion of the servo motor unit into a translation motion in the first direction or the second direction. are provided.
  • a table for mounting a workpiece a first actuator capable of vibrating the table in a first direction, and a table are applied in a second direction orthogonal to the first direction.
  • a first servo motor, a cylindrical casing, a second servo motor fixed in the casing, a frame fixed in the casing, and an output shaft of the servo motor are provided.
  • a torque applying unit having a speed reducer having an input shaft to be connected and an output shaft that decelerates and outputs the rotation of the input shaft and projects from the casing; and a subject is attached and one end portion of the speed reducer
  • a first gear box that transmits the output shaft and the rotational movement of the casing by a gear, and a connecting portion to which the other end of the first shaft and the other end of the second shaft are connected.
  • a second gearbox for transmitting rotational movement of the first shaft and the second shaft at the gear has, torsion test device having a is provided.
  • the power circulation is performed via the first gear box and the second gear box, the power loss is reduced as compared with the conventional configuration in which the power circulation is performed by the belt mechanism. A lower cost torsion tester is realized.
  • an output shaft a control unit that controls rotation of the output shaft so as to generate simulated power that simulates predetermined power, and torque that is instructed by the control unit is applied to the output shaft.
  • a weight applying unit supported rotatably, and a rotation driving unit that rotationally drives the load applying unit at a rotation speed instructed by the control unit, the weight applying unit having a rotation shaft connected to the output shaft.
  • a power simulator having a servo motor is provided.
  • an electric power simulator capable of accurately simulating torque fluctuation of a high frequency component even at a high rotational speed.
  • FIG. 1 is a side view of a rotary torsion test apparatus according to a first embodiment of the present invention. It is a longitudinal cross-sectional view of the load application part vicinity of the rotation torsion test apparatus which concerns on 1st Embodiment of this invention. It is a block diagram showing a schematic structure of a control system of a rotation torsion test device concerning a 1st embodiment of the present invention.
  • FIG. 1 is a side view of the biaxial output servomotor 150A.
  • the biaxial output servomotor 150A is a high output (rated output 37 kW) ultra-low inertia servomotor having two output shafts 150A2a and 150A2b.
  • the biaxial output servomotor 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 thereof.
  • a first bracket 150A3 and a second bracket 150A4 are attached to both ends of the main body frame 150A1 in the axial direction 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 provided with bearings 150A3b and 150A4b, respectively, which 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 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. Is given a rotational force.
  • the second bracket 150A4 incorporates a rotary encoder (not shown) that detects the rotation of the other end 150A2b of the drive shaft 150A2.
  • a pair of tap holes 150A3t and 150A4t for fixing the biaxial output servomotor 150A are provided on the lower surfaces of the first bracket 150A3 and the second bracket 150A4, respectively.
  • a fixing tap hole extending in parallel with the drive shaft is provided only on the mounting seat surface (the right side surface in FIG. 1) of the bracket on the load side (the side from which the output shaft protrudes).
  • a precision mechanical testing device that applies a dynamic load of a high frequency of several tens Hz (for example, 20 Hz) or more (for example, when using a high-output servomotor with a rated output of about 10 kW or more in a fatigue test apparatus or vibration test apparatus), the servomotor is oriented in a direction perpendicular to the drive shaft only by fixing on the mounting seat surface of the bracket. Cannot be fixed completely, for example, a vibration with a minute amplitude of about several ⁇ m to several tens of ⁇ m occurs, giving an error that cannot be ignored in the test results.
  • the present inventors have added significant tapping holes extending in the direction perpendicular to the drive shaft at two locations on the lower surface of each bracket, so that vibration noise becomes noticeable (for example, 1 We found that it was improved.
  • tapped holes are provided on the bottom surface of each bracket, and by using these tapped holes to fix the servo motor with bolts, vibration noise is reduced and higher precision machines are provided. The test becomes possible.
  • the servo motor 150A has a high rated output of 37 kW and a large amount of heat generated during operation, so that heat generated inside is radiated to the outside by water cooling.
  • Two tube joints 150A6 to which external piping for supplying and discharging cooling water is connected are provided on the upper part of the main body frame 150A1.
  • FIG. 2 is a side view of the servo motor unit 150 according to the embodiment of the present invention.
  • the servo motor unit 150 has one drive shaft 152.
  • the side from which the drive shaft 152 protrudes (the right side in FIG. 2) is referred to as the load side, and the opposite side is referred to as the anti-load side.
  • the 2-axis output servo motor 150A and the servo motor 150B each generate a torque of up to 350 N ⁇ m, and the inertial moment of the rotating part is suppressed to 10 ⁇ 2 (kg ⁇ m 2 ) or less. This 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, and the upper part of the main body frame 150B1 is an external for supplying and discharging cooling water.
  • Two tube joints 150B6 to which piping is connected are provided.
  • the anti-load side bracket 150B4 has substantially the same configuration as the second bracket 150A4 of the two-axis output servomotor 150A, but does not incorporate a rotary encoder, and the rotary encoder 150B5 is attached to the second bracket 150A4 as described later. Externally attached.
  • a pair of tap holes 150B3t and 150B4t are also provided on the lower surfaces of the load side bracket 150B3 and the anti-load side bracket 150B4, respectively.
  • the one end 150B2a on the load side of the drive shaft 150B2 passes through the load-side bracket 150B3, protrudes outside from the motor case, and becomes an output shaft 150B2a.
  • a rotary encoder 150B5 for detecting the angular position of the drive shaft 150B2 is attached to the mounting seat surface (left side surface in FIG. 2) of the anti-load side bracket 150B4, and the other end portion 150B2b of the drive shaft 150B2 is anti-load. It penetrates the side bracket 150B4 and is accommodated in the rotary encoder.
  • the output shaft 152B2a of the servomotor 150B and the second output shaft 150A2b of the two-axis output servomotor 150A are connected by a coupling 150C.
  • 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 with a predetermined interval by a connection flange 150D.
  • the connecting flange 150D has a cylindrical body portion 150D1 and two flange portions 150D2 that extend radially outward from both axial end portions of the body portion 150D1.
  • Each flange portion 150D2 is provided with a through hole for fixing a bolt at a position corresponding to a tap hole provided on the mounting seat surface of the load side bracket 150B3 and the second bracket 150A4. It is fixed to the bracket 150A4 with bolts.
  • the servo motor unit 150 includes two rotary encoders for detecting the angular position of the drive shaft 150B2 (one built in the second bracket 150A4 of the two-axis output servo motor 150A and the opposite load side of the servo motor 150B).
  • a rotary encoder 150B5) attached to the bracket 150B4 is provided, but usually only one rotary encoder is used for drive control of the servo motor unit 150, and the other is used for maintenance and monitoring of the drive state.
  • the long rotor connected by the coupling 150C is supported by the bearings at a total of four locations, that is, both ends in the longitudinal direction and two locations near the connection portion. Even if the rotor is long, it can be held with high rigidity and can operate stably. This makes it possible to generate large torque that fluctuates at a high frequency, which was impossible with conventional servo motors. Became. For example, an angular acceleration of 30000 rad / s 2 or more can be achieved with the servo motor unit 150 alone (no load state).
  • the servo motor unit 150 of the present embodiment is configured to connect two servo motors (two motor cases and two rotating shafts), but as shown in FIG. It is good also as a structure which provides one or more bearings in the middle of the longitudinal direction, and supports a drive shaft at both ends and one or more places in the middle.
  • FIG. 4 is a side view of the rotational torsion test apparatus 1 according to the first embodiment of the present invention.
  • the rotational torsion test apparatus 1 is an apparatus for performing a rotational torsion test using an automobile clutch as a specimen T1, and an input shaft and an output shaft (for example, a clutch cover and a clutch disk) of the specimen T1 while rotating the specimen T1.
  • the rotational torsion testing apparatus 1 includes a gantry 10 that supports each part of the rotational torsion testing apparatus 1, a load applying unit 100 that applies a predetermined torque to the specimen T1 while rotating together with the specimen T1, and a load applying part 100 that is rotatable.
  • Bearing portions 20, 30, and 40 that support the load, slip ring portions 50 and 60 that electrically connect the inside and outside of the load applying portion 100, a rotary encoder 70 that detects the rotational speed of the load applying portion 100, and a load applying portion
  • An inverter motor 80 that rotates and drives 100 in a set rotation direction and rotation speed, a drive pulley 91, and a drive belt (timing belt) 92 are provided.
  • the gantry 10 includes a lower base plate 11 and an upper base plate 12 that are arranged horizontally in the vertical direction, and a plurality of vertical support walls 13 that connect the lower base plate 11 and the upper stage 12.
  • a plurality of anti-vibration mounts 15 are attached to the lower surface of the lower base plate 11, and the gantry 10 is disposed 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. Further, bearing parts 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 sectional view of the load application unit 100 of the rotary torsion test apparatus 1.
  • the load applying unit 100 includes a stepped cylindrical casing 100a, a servo motor unit 150, a speed reducer 160, a connecting shaft 170, and a torque sensor 172 mounted in the casing 100a.
  • the casing 100 a includes a motor housing part (body part) 110 in which the servo motor unit 150 is housed, a shaft part 120 that is rotatably supported by the bearing part 20, and a shaft part 130 that is rotatably supported by the bearing part 30.
  • the shaft part 140 to which the slip ring 51 of the slip ring part 50 (FIG. 4) was attached is provided.
  • the motor housing part 110 and the shaft parts 120, 130, and 140 are substantially cylindrical members (or stepped cylinders whose diameter changes stepwise in the axial direction) each having a hollow part.
  • the motor housing part 110 is a member having the largest outer diameter for housing the servo motor unit 150 in the hollow part.
  • a shaft portion 120 is connected to one end portion (right end portion in FIG. 5) of the motor housing portion 110 on the specimen T1 side, and a shaft portion 130 is connected to the other end portion.
  • a shaft portion 140 is connected to the end portion of the shaft portion 130 opposite to the motor housing portion 110.
  • the shaft portion 140 is rotatably supported by the bearing portion 40 at the tip end portion (left end portion in FIG. 4).
  • the servo motor unit 150 is fixed to the motor housing portion 110 by a plurality of fixing rods 111.
  • Each fixed rod 111 includes a tap hole 150B3t provided in the load-side bracket 150B3 of the servo motor 150B and a tap hole 150B4t provided in the non-load-side bracket 150B4 shown in FIG. 2, and the first bracket of the biaxial output servomotor 150A.
  • the tap holes 150A3t provided in 150A3 and the tap holes 150A4t provided in the second bracket 150A4 are respectively screwed.
  • the drive shaft 152 of the servo motor unit 150 is connected to the input shaft of the speed reducer 160 via the coupling 154.
  • a connecting shaft 170 is connected to the output shaft of the speed reducer 160.
  • the reduction gear 160 includes a mounting flange 162, and the motor housing portion 110 and the shaft portion 120 are connected to each other by bolts (not shown) in a state where the mounting flange 162 is sandwiched between the motor housing portion 110 and the shaft portion 120.
  • the speed reducer 160 is fixed to the casing 100a.
  • the shaft portion 120 is a substantially stepped cylindrical member, has a pulley portion 121 having a large outer diameter on the motor housing portion 110 side, and is supported by the bearing portion 20 on the specimen T1 side so as to be rotatable.
  • a drive belt 92 is wound around the outer peripheral surface of the pulley portion 121 and the drive pulley 91 attached to the drive shaft 81 of the inverter motor 80, and the drive force of the inverter motor 80 is It is transmitted to the pulley part 121 by the drive belt 92 so that the load applying part 100 rotates.
  • a connecting portion between the speed reducer 160 and the connecting shaft 170 is accommodated in the pulley portion 121.
  • a compact device structure is realized without increasing the number of parts by using, as a pulley, a portion where the outer diameter needs to be increased in order to accommodate the connecting portion.
  • a torque sensor 172 is attached to the distal end portion (right end portion in FIG. 5) of the main shaft portion 122 of the shaft portion 120. Further, one surface (the right side surface in FIG. 5) of the torque sensor 172 is a seat 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 in the vicinity of both ends in the axial direction on the inner peripheral surface of the main shaft portion 122 of the shaft portion 120.
  • the connecting shaft 170 is rotatably supported in the shaft portion 120 by bearings 123 and 124.
  • the torque sensor 172 is formed in a substantially cylindrical shape having a hollow portion, and the distal end portion (the right end portion in FIG. 5) of the connecting shaft 170 passes through the hollow portion of the torque sensor 172 and protrudes to the outside.
  • the leading end protruding from the torque sensor 172 is fixed by being inserted into a shaft hole of a clutch disk (clutch hub) which is an output shaft of the specimen T1.
  • the servomotor unit 150 rotates the connecting shaft 170 with respect to the casing 100a of the load applying unit 100, thereby fixing the input shaft (clutch cover) of the specimen T1 fixed to the casing 100a and the connecting shaft 170.
  • a set dynamic or static torque can be applied to the output shaft (clutch disk) of the test specimen T1.
  • a rotary encoder 70 for detecting the rotational speed of the load applying unit 100 is disposed near the end of the shaft 130 (the left end in FIG. 4).
  • the slip ring 51 of the slip ring portion 50 is attached to the central portion of the shaft portion 140 in the axial direction.
  • a power line 150 ⁇ / b> W (FIG. 5) that supplies a drive current to the servo motor unit 150 is connected to the slip ring 51.
  • a power line 150 ⁇ / b> W 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 unit 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 portion 140 of the load application portion 100. Further, the brush 53 is fixed to the bearing portion 40 by a brush fixture 52.
  • the slip ring 51 has four electrode rings 51r arranged at equal intervals in the axial direction, and each brush 53 is arranged to face each electrode ring 51r. Each electrode ring 51r is connected to each power line 150W of the servo motor unit 150, and each brush 53 is connected to a servo motor drive unit 330 (described later).
  • each power line 150 ⁇ / b> W of the servo motor unit 150 is connected to the servo motor drive unit 330 through the slip ring unit 50.
  • the slip ring unit 50 introduces the drive current of the servo motor unit 150 supplied from the servo motor drive unit 330 into the rotating load applying unit 100.
  • a slip ring (not shown) of the slip ring portion 60 is attached to the tip end 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 unit 60.
  • the torque sensor 172 or the rotary encoder 150B5 built in the servo motor unit 150 (FIG. 2). ) And the like are output to the outside via the slip ring unit 60.
  • the communication line 150W ′ through which the weak current flows and the power line 150W through which the large current flows are connected to the external wiring by using separate slip rings arranged at a certain distance, It is possible to effectively prevent noise from being mixed into the communication signal.
  • the slip ring part 60 is provided in the surface on the opposite side to the slip ring part 50 side of the bearing part 40. As shown in FIG. With this configuration, the bearing portion 40 can also obtain an effect of shielding the slip ring portion 60 from electromagnetic noise generated in the slip ring portion 50.
  • FIG. 6 is a block diagram illustrating a schematic configuration of a control system of the rotational torsion test apparatus 1.
  • the rotary torsion test apparatus 1 includes a control unit C1 for controlling the entire rotary torsion test apparatus 1, a setting unit 370 for setting test conditions, and set test conditions (waveforms of torque and torsion angle applied to a specimen). And the like, and a waveform generation unit 320 that calculates a drive amount waveform of the servo motor unit 150 based on the control unit C1, and a servo motor that generates a drive current of the servo motor unit 150 based on the control of the control unit C1.
  • Torque measurement that calculates the torque applied to the specimen based on the signal from the drive unit 330, the inverter motor drive unit 340 that generates the drive current of the inverter motor 80 based on the control of the control unit C1, and the torque sensor 172 With load based on unit 350 and rotary encoder 70 signal And a rotational speed measuring unit 360 for calculating the rotational speed of the parts 100.
  • the setting unit 370 includes a user input interface such as a touch panel (not shown), an exchangeable recording media reader such as a CD-ROM drive, an external input interface such as GPIB (General Purpose Interface Bus) and USB (Universal Serial Bus). It has a network interface.
  • the setting unit 370 receives user input received via a user input interface, data read from a replaceable 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 acquired from the server via Note that the rotational torsion test apparatus 1 of the present embodiment has a twist applied to the specimen T1 as a twist angle applied to the specimen T1 (that is, a servo motor unit detected by a rotary encoder 150B5 built in the servo motor unit 150). 150, the displacement control controlled based on the driving amount), and the torque control controlled based on the torque applied to the specimen T1 (ie, detected by the torque sensor 172).
  • the control unit 370 can set which control method is used.
  • the control unit C1 instructs the inverter motor drive unit 340 to rotate the inverter motor 80 based on the set value of the rotation speed of the specimen T1 acquired from the setting unit 370.
  • 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.
  • 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.
  • the signal of the built-in rotary encoder built in the servo motor unit 150 is sent to the control unit C1, the waveform generation unit 320, and the servo motor drive unit 330.
  • the waveform generation unit 320 calculates a measured value of the rotation speed of the servo motor unit 150 from a signal of 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 the torque (the drive amount of the servo motor unit 150 in the case of displacement control) with the measured value, and sends the control unit C1 so that the two match.
  • the set value of the drive amount of the servo motor unit 150 to be sent is corrected.
  • the measured value of the rotational speed of the load applying unit 100 calculated by the rotational speed measurement unit 360 based on the signal of the rotary encoder 70 is sent to the control unit C1.
  • the control unit C1 compares the set value of the rotational speed of the load applying unit 100 and the measured value, and feedback-controls the frequency of the drive current sent to the inverter motor 80 so that they match.
  • 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 so that the drive amount approaches the target value. Feedback control of the drive current sent to
  • control unit C1 includes a hard disk device (not shown) for storing test data, and the rotation speed of the specimen T1 and the twist angle applied to the specimen T1 (rotation angle of the servo motor unit 150).
  • the data of each measured value of the torsional load is recorded in the hard disk device.
  • the time change of each measurement value is recorded over the entire period from the start to the end of the test.
  • the output of the inverter motor 80 for controlling the rotational speed and the output of the servo motor unit 150 for controlling the torque are combined so that the rotational speed and the torque can be controlled independently and with high accuracy. It is configured.
  • a servo motor unit 150 in which a plurality of ultra-low inertia servo motors are connected in series, it becomes possible to control a large torque that fluctuates with a high angular jerk (angular jerk). Output (especially torque vibration of a reciprocating engine) can be accurately reproduced.
  • the responsiveness of torque control is improved, and a response time of 3 ms or less is achieved.
  • the rotary drive device having such a configuration is not limited to a rotary torsion test device, and can be used as a power source for various devices.
  • it can be used as a power simulator (simulated engine) capable of outputting power simulating various types of engine outputs in a test apparatus for automobiles (or automobile parts).
  • the torque generated by the servo motor unit 150 is controlled with high accuracy, the reproducibility is extremely high and there is no individual difference. Therefore, it is possible to give a more uniform load than a test using a real engine as in the prior art, and a test with higher reproducibility becomes possible.
  • Modification of the first embodiment 7 and 8 are external views of power simulators 1a and 1b in which a part of the rotational torsion test apparatus 1 according to the first embodiment of the present invention described above is changed.
  • the bearing portion 1020 has the same configuration as the bearing portion 1020 of the second embodiment to be described later, and incorporates a torque sensor that detects the torque of the connecting shaft 170 (the connecting shaft 1170 in the second embodiment).
  • the slip ring 1401 is attached to the bearing portion 1020 and takes out a signal output from a torque sensor built in the bearing portion 1020 to the outside.
  • the attachment portion 173 is a flange joint and is attached to the distal end portion of the connecting shaft 170.
  • the power simulator 1a configured as described above includes engine accessories (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 and tires.
  • the inverter motor 80 is disposed on the lower base plate 11 and the load applying unit 100 is disposed on the upper base plate 12.
  • a single-stage structure in which the inverter motor 80 and the load applying unit 100 are arranged on the same base plate 10X may be used.
  • the two-stage structure is effective for reducing the installation area.
  • the one-stage structure is advantageous in terms of cost reduction because of its simple structure, and is advantageous in improving the rigidity of the base (that is, vibration resistance characteristics and load resistance characteristics).
  • the test apparatus 100E described below is for a starter motor that performs a durability test by applying a rotational driving force simulating an engine load generated by the power simulator 1a to a ring gear T1 and a starter motor T2 of a flywheel that is a specimen. Test equipment.
  • the test apparatus 100E holds the starter motor and the ring gear of the flywheel in an engaged state, gives the rotational driving force of the power simulator 1a to the starter motor, and performs a durability test of the starter motor and the ring gear.
  • FIG. 9 is a side view of the test apparatus 100E.
  • FIG. 10 is an enlarged view of the vicinity of the specimen (ring gear T1, starter motor T2).
  • the test apparatus 100E is obtained by adding a support portion S for holding a specimen to the power simulator 1a. That is, the test apparatus 100E includes the load applying unit 100 rotatably supported by the inverter motor 80 attached to the lower base plate 11 of the gantry 10 and the bearing portions 1020, 30 and 40 attached to the upper base plate 12. I have.
  • the load applying unit 100 is rotationally driven by the inverter motor 80.
  • the load applying unit 100 includes a servo motor unit 150 and a speed reducer, and an output shaft of the servo motor unit 150 is connected to a connecting shaft 170 protruding outside the load applying unit 100 via the speed reducer.
  • the connecting shaft 170 is disposed coaxially with the rotation axis of the load applying unit 100, and the rotation of the connecting shaft 170 is obtained by adding the rotation of the servo motor unit 150 to the rotation of the load applying unit 100 by the inverter motor 80. .
  • the inverter motor 80 reproduces the engine speed
  • the servo motor unit 150 reproduces the engine high speed fluctuation torque (high angular acceleration, high angular jerk (angular jerk)).
  • the attachment part 173 for attaching ring gear T1 is attached to the front-end
  • a support portion S that supports the starter motor T2 is attached to the upper base plate 12 of the gantry 10.
  • the ring gear T1 and the pinion gear of the starter motor T2 are engaged.
  • the test is performed by driving the power simulator 1a of the test apparatus 100E and applying the rotation simulating the rotation of the engine to the ring gear T1 and the starter motor T2.
  • the rotational torsion test apparatus 1000 is an apparatus for performing a rotational torsion test using an automobile propeller shaft as a specimen T2, and a fixed or variable torque set between an input shaft and an output shaft of the propeller shaft while rotating the propeller shaft. Can be added.
  • FIG. 11 is a plan view of the rotary torsion test apparatus 1000
  • FIG. 12 is a side view of the rotary torsion test apparatus 1000 (viewed from the lower side to the upper side in FIG. 11).
  • FIG. 13 is a longitudinal sectional view in the vicinity of a load applying portion 1100 described later. Note that the control system of the rotational torsion test apparatus 1000 has the same schematic configuration as that of the first embodiment shown in FIG.
  • the rotating torsion test apparatus 1000 includes four bases 1011, 1012, 1013, and 1014 that support each part of the rotating torsion test apparatus 1000, and both ends of the specimen T2 while rotating together with the specimen T2.
  • a load applying unit 1100 that applies a predetermined torque to the bearing, bearings 1020, 1030, and 1040 that rotatably support the load applying unit 1100, and a slip ring unit 1050 that electrically connects wiring inside and outside the load applying unit 1100, 1060 and 1400, a rotary encoder 1070 for detecting the rotation speed of the load applying unit 1100, and one end portion (the right end portion in FIG.
  • Inverter motor 1080 and the driving force of inverter motor 1080 for applying load A driving force transmission unit 1190 (a driving pulley 1191, a driving belt (timing belt) 1192, and a driven pulley 1193) that transmits the driving force to 100, and a driving force transmission unit 1200 that transmits the driving force of the inverter motor 1080 to one end of the specimen T2. I have.
  • the driving force transmission unit 1200 includes a bearing portion 1210, a driving shaft 1212, a relay shaft 1220, a bearing portion 1230, a driving shaft 1232, a driving pulley 1234, a bearing portion 1240, a driving shaft 1242, a driven pulley 1244, and a driving belt (timing belt) 1250. And a work mounting portion 1280.
  • the bearing units 1020, 1030, and 1040, the slip ring unit 1050, the slip ring unit 1060, the rotary encoder 1070, the inverter motor 1080, and the drive pulley 1091 in the rotary torsion testing apparatus 1000 are respectively the rotational torsion testing apparatus 1 of the first embodiment.
  • the bearing parts 20, 30, 40, slip ring part 50, slip ring part 60, rotary encoder 70, inverter motor 80, and drive pulley 91 are configured similarly.
  • the load applying unit 1100 has the same configuration as the load applying unit 100 of the first embodiment except for a shaft portion 1120, a connecting shaft 1170, a work attachment portion 1180, and a slip ring portion 1400, which will be described later.
  • the drive belt 1192 is different from the configuration of the drive belt 92 of the first embodiment in that the drive belt 1192 is hung on the driven pulley 1193 on the driven side, but the other configurations are the same as the drive belt 92.
  • the same or similar reference numerals are used for the same or similar components as those in the first embodiment, and detailed description thereof is omitted, and differences in configuration from the first embodiment are described. The explanation is centered.
  • the four bases 1011, 1012, 1013 and 1014 are arranged on the same flat floor F and fixed by fixing bolts (not shown).
  • an inverter motor 1080 and a bearing portion 1210 are fixed.
  • the bearing portions 1020, 1030, and 1040 that support the load applying portion 1100 and the support frame 1402 of the slip ring portion 1400 are fixed.
  • a bearing portion 1230 is fixed to the base 1013
  • a bearing portion 1240 is fixed to the base 1014.
  • the bases 1013 and 1014 can be moved in the axial direction of the bearing portion 1230 or 1240 according to the length of the specimen T1 by loosening the fixing bolts.
  • the connecting shaft 1170 of the load applying portion 1100 protrudes from the tip end portion (right end in FIG. 13) of the shaft portion 1120 to the outside, and the work attachment portion (flange joint) is connected to the tip end portion (right end portion in FIG. 13) of the connecting shaft 1170. ) 1180 is fixed.
  • a slip ring 1401 having a plurality of electrode rings is attached to a central portion in the axial direction of a portion protruding from the shaft portion 1120 of the connecting shaft 1170.
  • an annular narrowed portion 1172 having a thin outer diameter is formed in a portion accommodated in the shaft portion 1120 of the connecting shaft 1170, and a circumferential surface of the narrowed portion 1172 is formed.
  • a strain gauge 1174 is attached.
  • the connecting shaft 1170 is a cylindrical member having a hollow portion (not shown) penetrating on the central axis, and an insertion hole (not shown) communicating with the hollow portion is formed in the narrowed portion 1172.
  • a lead (not shown) of the strain gauge 1174 is passed through the insertion hole and the hollow portion formed in the connecting shaft 1170 and is connected to each electrode ring of the slip ring 1401.
  • a wiring groove extending from the narrowed portion 1172 to the slip ring 1401 is provided on the peripheral surface of the connecting shaft 1170, and the lead of the strain gauge 1174 is routed to the slip ring 1401 through the wiring groove. It is good also as a structure.
  • the brush part 1403 fixed on the support frame 1402 is arranged at the lower part of the slip ring 1401.
  • the brush portion 1403 includes a plurality of brushes arranged to face each electrode ring of the slip ring 1401 so as to be in contact therewith.
  • Each brush terminal is connected to a torque measuring unit 1350 (described later) by a wire (not shown).
  • the bearing portions 1210, 1230, and 1240 respectively support the drive shafts 1212, 1232, and 1242 so as to be rotatable.
  • 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.
  • one end portion (left end portion in FIG. 11) of the drive shaft 1232 is connected to the other end portion (right end portion in FIG. 11) of the drive shaft 1212 via the relay shaft 1220.
  • a drive pulley 1234 is attached to the other end of the drive shaft 1232 (right end in FIG.
  • a driven pulley 1244 is attached to one end of the drive shaft 1242 (right end in FIG. 11).
  • a driving belt 1250 is stretched between the driving pulley 1234 and the driven pulley 1244.
  • a work attachment portion (flange joint) 1280 for fixing one end portion of the specimen T2 is attached to the other end portion (left end portion in FIG. 11) of the drive shaft 1242.
  • the driving force of the inverter motor 1080 is transmitted through the above-described driving force transmission unit 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 workpiece attachment portion 1280 is transmitted to the workpiece attachment portion 1280, and the workpiece attachment portion 1280 is rotated with the set rotation direction and rotation speed.
  • the driving force of the inverter motor 1080 is transmitted to the load applying unit 1100 via the driving force transmitting unit 1190 (that is, the driving pulley 1191, the driving belt 1192, and the driven pulley 1193), and the load applying unit 1100 and the work attaching unit are transmitted.
  • 1280 and 1280 are rotated synchronously (that is, always at the same rotational speed and the same phase).
  • the drive shaft 1212 and the load applying unit 1100, the drive shaft 1232, and the drive shaft 1242 that are arranged in parallel to each other are connected by the drive belts 1192 and 1250, respectively, so that a power circulation system is configured.
  • the present invention is not limited to this configuration, and a configuration in which power is transmitted using a gear device instead of a drive belt as in the third to seventh embodiments described below is also included in the scope of the present invention. It is.
  • FIG. 14 (a) is a top view of a torsion test apparatus according to the third embodiment of the present invention.
  • FIG. 14B is a side view of the torsion test apparatus according to this embodiment.
  • a workpiece rotating servomotor 121, a torque applying unit 130, a first gear box 141, and a second gear box 142 are fixed on a base 110. It becomes the composition.
  • the first gear box 141 includes four shaft connecting portions 141a1, 141a2, 141b1, and 141b2.
  • the second gear box 142 includes two shaft connecting portions 142a and 142b.
  • a drive pulley 122 is attached to the output shaft 121a of the workpiece rotating servomotor 121. Further, the shaft 123 a of the driven pulley 123 is attached to the shaft connecting portion 141 a 1 of the first gear box 141. In addition, an endless belt 124 is hung on the driving pulley 122 and the driven pulley 123, and the driven pulley 123 can be rotated at a desired rotational speed by driving the workpiece rotating servo motor 121. .
  • the torque applying unit 130 is connected to the shaft connecting portions 141b1 and 141b2.
  • the configuration of the torque applying unit 130 will be described below.
  • FIG. 15 is a side sectional view of the torque applying unit 130 and the first gear box 141 of the present embodiment.
  • the torque applying unit 130 includes a casing 131, a torque applying servo motor unit 132 and a speed reducer 133 fixed in the casing 131.
  • the servo motor unit 132 for torque application 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. Also good.
  • a tubular portion 131a is formed on one end side (right side in the drawing) of the casing 131 in the axial direction. The tubular portion 131a is inserted into the first gear box 141 via the shaft connecting portion 141b1, and is supported rotatably in the first gear box 141.
  • a gear 141b3 is attached to the tubular portion 131a.
  • the speed reducer 133 has an input shaft 133a and an output shaft 133b, decelerates the rotational motion input to the input shaft 133a, and outputs it to the output shaft 133b.
  • the input shaft 133 a of the speed reducer 133 is coupled to the output shaft 132 a of the torque applying servo motor unit 132 by a coupling 134.
  • the output shaft 133b of the speed reducer 133 is rotatably supported inside the tubular portion 131a of the casing 131, and protrudes from the distal end portion of the tubular portion 131a.
  • the output shaft 133b of the speed reducer 133 protruding from the tubular portion 131a is connected to the shaft connecting portion 141b2 of the first gear box 141.
  • the output shaft 133b of the speed reducer 133 is coupled to the input shaft W1a of the transmission unit W1 to be tested via a coupling 151.
  • the output shaft W1b of the transmission unit W1 is connected to the shaft connecting portion 142b of the second gear box 142 via the torque sensor 160.
  • the output shaft W2b of the transmission unit W2 is connected to the shaft connecting portion 142a of the second gear box 142 via the relay shaft 143.
  • the input shaft W2a of the transmission unit W2 is connected to the shaft connecting portion 141a2 of the first gear box 141 via the coupling 152.
  • the shaft 123 a of the driven pulley 123 attached to the shaft connection portion 141 a 1 of the first gear box 141 and the shaft attached to the shaft connection portion 141 a 2 are connected via the coupling 153 inside the first gear box 141.
  • 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 gear box 141 on the tubular portion 131a connected to the shaft connecting portion 141b1. As shown in FIG.
  • the gear 141a3 and the gear 141b3 are meshed with each other via the intermediate gear 141i, the shaft connected to the shaft connecting portions 141a1 and 141a2, and the shaft connected to the shaft connecting portion 141b1. Rotational motion can be transmitted to each other. Since the intermediate gear 141i is interposed between the gear 141a3 and the gear 141b3, the driven pulley 123, the relay shaft 143, and the casing 131 of the torque applying unit 130 rotate in the same direction.
  • a gear 142a1 is attached to a shaft portion (one end portion of the relay shaft 143) connected to the shaft connection portion 142a.
  • a gear 142b1 is connected to the shaft connected to the shaft connection 142b.
  • the gears 142a1 and 142b1 mesh with each other through the intermediate gear 142i inside the second gear box 142, and between the shaft connected to the shaft connecting portion 142a and the shaft connected to the shaft connecting portion 142b, Rotational motion can be transmitted to each other. Since the intermediate gear 142i is interposed between the gear 142a1 and the gear 142b1, the shaft connected to the shaft connecting portion 142a and the shaft connected to the shaft connecting portion 142b rotate in the same direction. It has become.
  • Transmission unit W2 is the same type (same reduction ratio) as transmission unit W1.
  • 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 gear box 141 are substantially equal.
  • the transmission unit W2 is a kind of dummy work used for adjusting the rotational speed of the shaft connected to the shaft connecting portions 141a2 and 141b2 as described above, and is not an object of the torsion test.
  • the workpiece rotating servomotor 121 is driven at a constant speed, and the output shaft 132a is reciprocally driven by the torque applying servomotor unit 132 (FIG. 15), whereby the input shaft W1a of the transmission unit W1 is driven. It is possible to apply torque that varies periodically while rotating.
  • FIG. 16 is a top view of a torsion test apparatus according to the fourth embodiment of the present invention.
  • the torsion test apparatus 100A according to the present embodiment does not use a dummy work, and the coupling 152 and the shaft connection portion 142a of the second gear box 142 are directly connected by the relay shaft 143A. Is the same as the torsional testing apparatus 100 of the third embodiment.
  • elements having the same or similar functions as those of the third embodiment are denoted by the same or similar reference numerals, and redundant description is omitted.
  • the rotation speed of the relay shaft 143A (that is, the rotation speed of the casing 131 of the torque application unit 130) and the rotation speed of the shaft connected to the shaft connection portion 141b2 of the first gear box 141 (that is, transmission)
  • the rotational speed of the input shaft W1a of the unit W1 is different.
  • 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 rotational speed at the input / output shaft of the transmission unit W1.
  • the rotation speed of the servo motor 121 for rotating the workpiece is set so that the rotation speed of the servo motor 121 for the workpiece rotation is set to 2857 rpm. Is set, the rotational speed of the input shaft W1a of the transmission unit W1 can be set to 4000 rpm.
  • the torsion test of the transmission unit W1 can be performed without using a dummy work while performing power circulation.
  • the gear ratio of the transmission unit W1 can be changed during the torsion test. is there.
  • the rotation speed of the torque applying servo motor unit 131 can be suddenly changed in synchronism with the change in the rotation speed of the output shaft W1b due to the 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 gear boxes 141 and 142 and the transmission unit W1 are not excessively loaded and damaged.
  • the transmission unit is a subject (work).
  • the present invention is not limited to the above configuration, and a torsion test can be performed on other types of workpieces.
  • a torsion test apparatus according to a fifth embodiment of the present invention described below performs a torsion test using the entire power transmission system of the FR vehicle as a workpiece.
  • FIG. 17 is a top view of a torsion test apparatus according to the fifth embodiment of the present invention.
  • the torsion test apparatus 100B according to the present embodiment performs a torsion test on a power transmission system W3 of an FR vehicle including a transmission unit TR1, a propeller shaft PS, and a differential gear DG1. is there.
  • the second gearbox (142B1, 142B2) for returning the output of the differential gear DG1 to the first gearbox 141B.
  • relay shafts (143B1, 143B2) are provided in two systems. 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 gear box 141B includes shaft connecting portions 141Bb1 and 141Bb2 to which the tubular portion 131a of the casing 131 of the torque applying unit 130 and the input shaft TR1a of the transmission unit TR1 are respectively attached (the shaft connecting portions 141b1 and 141b2 of the third embodiment). And the shaft connecting portion 143Bc connected to the relay shaft 143B2 in addition to the shaft connecting portions 141Ba1 and 141Ba2 to which the output shaft 121a of the workpiece rotating servomotor 121 and the relay shaft 143B1 are connected. Further, the output shaft 121a of the workpiece rotating servomotor 121 and the relay shaft 143B1 are connected via a coupling 153B disposed in the first gear box 141. Further, the input shaft TR1a of the transmission unit TR1 and the output shaft 133b of the speed reducer 133 of the torque applying unit 130 are connected via a coupling 151B disposed in the first gear box 141.
  • the shafts connected to the shaft connecting portions 141Ba1, 141Bb1, and 141Bc are connected to each other via gears and intermediate gears (not shown) separately attached to the respective shafts, and when the workpiece rotating servo motor 121 is driven.
  • the relay shafts 143B1 and 143B2 and the casing 131 of the torque applying unit 130 are rotated.
  • the torque application motor is made up to compensate for the difference in rotational speed.
  • the number of rotations 131 (FIG. 15) is controlled.
  • a torsion test apparatus In the configuration of the present invention, it is also possible to use a power transmission system for an FF vehicle as a workpiece.
  • a torsion test apparatus According to a sixth embodiment of the present invention described below performs a torsion test on a power transmission system of an FF vehicle.
  • FIG. 18 is a top view of a torsion test apparatus 100C according to the sixth embodiment of the present invention.
  • the torsion test apparatus 100C of the present embodiment performs a torsion test using a power transmission system W4 for an FF vehicle in which a transmission unit TR2 incorporating a torque converter TC and a differential gear DG2 are integrated as a workpiece. Is what you do.
  • 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 in parallel. is there. Therefore, in the present 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. is doing.
  • the first gear box 141C of the present embodiment includes shaft connecting portions 141Cb1 and 141Cb2 to which the tubular portion 131a of the casing 131 of the torque applying unit 130 and the input shaft TR2a of the transmission unit TR2 are respectively attached, It has shaft connecting portions 141Ca1, 141Ca2 to which the output shaft 121a of the servo motor 121 for rotation and the output shaft DG2a of the differential gear DG2 are connected, and a shaft connecting portion 143Cc connected to the relay shaft 143C.
  • the output shaft 121a of the workpiece rotating servomotor 121 and the output shaft DG2a of the differential gear DG2 are connected by a coupling 153C disposed in the first gear box 141C. Further, the output shaft 133b of the speed reducer 133 of the torque applying unit 130 and the input shaft TR2a of the transmission unit TR2 are connected by a coupling 151C disposed in the first gear box 141C.
  • the shafts connected to the shaft connecting portions 141Ca1, 141Cb1, 141Cc are connected to each other via gears separately attached to the respective shafts.
  • the output shaft DG2a of the differential gear DG2 is driven.
  • the casing 131 of the relay shaft 143C and the torque application unit 130 is rotated.
  • the rotational speed of the input shaft TR2a of the transmission unit TR2 is different from the rotational speed of the output shaft DG2a of the differential gear DG2 and the relay shaft 143C.
  • the rotational speed of the torque application motor 131 (FIG. 15) is controlled so as to compensate for the difference in number.
  • FIG. 19 is an external view of a rotary torsion test apparatus 100B according to the seventh embodiment of the present invention. As shown in FIG. 19, the torsion test apparatus 100B according to the present embodiment performs a rotational torsion test on a differential gear DG1.
  • the output shaft of the differential gear DG1 has two systems (DG1a, DG1b), the second gearbox (142B1, 142B2) for returning the output of the differential gear DG1 to the first gearbox 141B.
  • Two bevel gearboxes 144B1, 144B2
  • relay shafts 143B1, 143B2
  • the output shafts DG1a and DG1b of the differential gear DG1 are connected to the relay shafts 143B1 and 143B2 via the second gear boxes 142B1 and 142B2 and the bevel gear boxes 144B1 and 144B2, respectively.
  • 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.
  • relay shafts 143B1 and 143B2 are connected to the gears 141Ba and 141Bc, respectively. Accordingly, when the inverter motor 80 is driven, the relay shafts 143B1 and 143B2 and the casing 131 of the torque applying unit 130 are rotated.
  • the output shafts DG1a and DG1b and the input shaft DG1c of the differential gear DG1 are connected to the shaft portions of the gearboxes 142B1 and 142B2 and the torque applying unit 130 via torque sensors 172a, 172b and 172c, respectively.
  • the torque sensors 172a, 172b, and 172c are respectively shown in FIG. 13 (second embodiment), with a shaft 1170 having a strain gauge 1174 attached to a constricted portion 1172 at a bearing portion 1020 (without the shaft portion 1120 interposed). (Directly supported).
  • the servo motor unit incorporated in the torque applying unit 130 to compensate for this rotational speed difference.
  • a rotational speed of 150 is controlled.
  • a torsion test apparatus is a power circulation type test apparatus that performs a rotational torsion test on a power transmission system of an FF vehicle.
  • FIG. 20 is an external view of a torsion test apparatus 100C according to the eighth embodiment of the present invention. As shown in FIG. 20, the torsion test apparatus 100C of the present embodiment performs a rotational torsion test on a transmission unit TR for an FF vehicle.
  • the input shaft TRa and the output shafts TRb, TRc of the transmission unit TR are all connected to the first gear box 141C via the torque sensors 172b, 172b, 172c without being decelerated. ing. Further, the input shaft TRa and the output shafts TRb and TRc of the transmission unit TR are disposed substantially parallel to each other. Therefore, in the present embodiment, the input shaft TRa and one output shaft TRb of the transmission unit TR are directly connected to the first gear box 141C, and the other output shaft TRc is connected to the second gear box 142C and the output shaft TRc. Are connected to the first gear box 141C via a relay shaft 143C disposed substantially parallel to the first gear box 141C. That is, the driving force of the output shaft TRc is turned 180 ° by the second gear box 142C and then transmitted to the first gear box 141C by the relay shaft 143C.
  • the first gear box 141C of the present embodiment includes a gear 141Cb and gears 141Ca and 141Cc that engage with the gear 141Cb, respectively.
  • the gear 141Ca is engaged with the gear 141Cb via the pinion gear, and the rotation of the gear 141Cb is decelerated and transmitted to the gear 141Ca.
  • the tubular portion of the casing of the torque applying unit 130 is connected to the gear 141Ca, and the output shaft of the inverter motor 80 is connected to the gear 141Cc via a timing belt.
  • the transmission unit TR since the transmission unit TR has a reduction ratio, the rotational speed of the input shaft TRa and the rotational speeds of the output shafts TRb and TRc are different. Therefore, the rotational speed of the servo motor unit 150 built in the torque applying unit 130 is controlled so as to compensate for the difference in rotational 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 test apparatus using a power transmission system such as a transmission unit as a work.
  • the present invention is not limited to the above configuration.
  • the present invention can be applied to various tests of tires.
  • FIG. 21 is a top view of a tire wear test apparatus 100D according to the ninth embodiment of the present invention.
  • the tire wear test apparatus 100D has a power circulation mechanism having the same configuration as that of the third embodiment described above.
  • the first gear box 141D includes four shaft connecting portions 141Da1, 141Da2, 141Db1, and 141Db2.
  • the second gear box 142D includes two shaft connecting portions 142Da and 142Db.
  • both end portions of the shaft 145 serving as the rotation shaft of the rotary drum DR as the simulated road surface are connected to the shaft connection portion 141Da2 of the first gear box 141D and the shaft connection portion 142Da of the second gear box 142D, respectively.
  • both end portions of the shaft 144 serving as the rotation axis of the tire T that is the subject are connected to the shaft connecting portion 141Db2 of the first gear box 141D and the shaft connecting portion 142Db of the second gear box 142D, respectively.
  • the rotation of the output shaft 121a of the workpiece rotating servomotor 121 for driving the tire T and the rotating drum DR is performed by a belt mechanism composed of a driving pulley 122, a driven pulley 123, and an endless belt 124.
  • the shaft 123a of the driven pulley 123 is rotationally driven.
  • the shaft 123a is connected to the shaft connecting portion 141a of the first gear box 141D.
  • the tubular portion 131a of the casing 131 of the torque application unit 130 is connected to the shaft connection portion 141Db1 of the first gear box 141D. Further, the output shaft 133b of the speed reducer 133 of the torque application unit 130 is coupled to one end portion of the shaft 144 for the tire T via a coupling 151D disposed inside the first gear box 141D.
  • One end of the shaft 145 for the drum DR that is attached to the first gear box 141D is coupled to the shaft 123a of the driven pulley 123 via a coupling 153D disposed inside the first gear box 141D. Yes.
  • the shaft 123a attached to the shaft connection portion 141Da1 of the first gear box 141D and the shaft (tubular portion 131a) attached to the shaft connection portion 141Db1 are connected to different gears provided inside the first gear box 141, respectively. It has become so. These gears mesh with each other inside the second gear box 142, and when the servo motor 121 for rotating the workpiece is driven, the drum DR shaft 145 and the casing 131 of the torque applying unit 130 rotate. Yes.
  • the shaft 145 attached to the shaft connection portion 142Da of the second gear box 142 and the shaft 144 attached to the shaft connection portion 142Db are connected to different gears provided inside the second gear box 142, respectively. It has become. These gears mesh with each other inside the second gear box 142, and the rotation of the shaft 144 is transmitted to the shaft 145 by the second gear box 142.
  • the gear ratio in the first gear box 141D and the second gear box 142D is the same as that of the rotary drum DR and the tire T. It is set to a value according to the ratio of the diameters.
  • the tire T and the drum DR are rotated by setting the tire T on the shaft 144 and driving the servo motor 121 for rotation.
  • the torque applying servo motor unit 131 (FIG. 2) of the torque applying unit 130 is driven to apply a forward or reverse torque to the tire T, thereby simulating the acceleration / deceleration of the automobile.
  • a test can be performed.
  • a tire testing apparatus is a testing apparatus that performs a tire wear test, a durability test, a running stability test, and the like.
  • the tire test apparatus 100D of the present embodiment includes a rotating drum 10 having a simulated road surface formed on the outer peripheral surface, an inverter motor 80 that rotationally drives the casing of the rotating drum 10 and the torque applying unit 130, an alignment control mechanism 160, and an alignment.
  • a torque applying unit 130 that applies torque to the tire T rotatably supported by the control mechanism 160 is provided.
  • the torque application unit 130 includes a servo motor unit 150 having the same configuration as that of the first embodiment.
  • the rotating drum 10 is rotatably supported by a pair of bearings 11a.
  • a pulley 12 a is attached to the output shaft of the inverter motor 80, and a pulley 12 b is attached to one shaft of the rotary drum 10.
  • the pulley 12a and the pulley 12b are connected by a drive belt.
  • a pulley 12 c is attached to the other shaft of the rotating drum 10 via a relay shaft 13.
  • the relay shaft 13 is rotatably supported by a bearing 11b in the vicinity of one end where the pulley is attached.
  • the pulley 12c is connected to the pulley 12d by a drive belt.
  • the pulley 12d is fixed coaxially to the pulley 12e, and is rotatably supported by the bearing 11c (FIG. 27) together with the pulley 12e.
  • the pulley 12e is connected to the tubular portion of the casing of the torque applying unit 130 by a drive belt.
  • the drive shaft of the servo motor unit 150 built in the torque applying unit 130 is connected to the wheel of the alignment control mechanism 160 to which the tire T is mounted via the relay shaft 14 and the flexible coupling.
  • the rotating drum 10 rotates and the casing of the torque applying unit 130 connected to the inverter motor 80 via the rotating drum 10 rotates. Further, the rotating drum 10 and the tire T are rotated in opposite directions so that the peripheral speed at the contact portion is the same when the torque applying unit 130 is not operated. In addition, by operating the torque application unit 130, dynamic driving force and braking force can be applied to the tire T.
  • the alignment control mechanism 160 of the present embodiment supports the tire T as a specimen in a state of being mounted on the wheel, presses the tread portion against the simulated road surface of the rotating drum 10, and aligns the tire T with the simulated road surface or the tire. This is a mechanism for adjusting the load (ground pressure) to a set state.
  • the alignment control mechanism 160 tilts the rotation axis of the tire T around the normal of the simulated road surface, and the tire load adjustment unit 161 that adjusts the tire load by moving the position of the rotation axis of the tire T in the radial direction of the rotary drum 10.
  • a slip angle adjustment unit 162 that adjusts the slip angle of the tire T with respect to the simulated road surface, a camber angle adjustment unit 163 that adjusts the camber angle by inclining the rotation axis of the tire T with respect to the rotation axis of the rotary drum 10, and the tire A traverse device 164 for moving T in the rotation axis direction is provided.
  • the tire T and the drum DR are rotated at the same peripheral speed by setting the tire T in the tire test apparatus 100D having the above-described configuration and driving the inverter motor 80 for rotational driving.
  • the servo motor unit 150 of the torque applying unit 130 is driven to apply a driving force and a braking force to the tire T, thereby simulating an actual running state, a tire wear test, a durability test, and a running stability. It becomes possible to conduct tests and the like.
  • FIG. 24 is an external view of a power absorption durability test apparatus 100F for an FR transmission according to an eleventh embodiment of the present invention.
  • the test apparatus 100F includes a power simulator 100X including an inverter motor 80 and a load applying unit 100 including a servo motor unit 150, a support unit S that supports a case of an FR transmission T that is a specimen, and a torque sensor 172a. , 172b and two power absorption servomotors 90A and 90B.
  • the input shaft of the FR transmission T is connected to the output shaft of the load applying unit 100 via the torque sensor 172a.
  • the output shaft To of the FR transmission T is connected to the pulley unit 180 via the torque sensor 172b.
  • the torque sensors 172a, 172b have the same configuration as the torque sensors 172a, 172b, 172c of the seventh embodiment.
  • the pulley unit 180 is connected to two power absorption servomotors 90A and 90B by two drive belts.
  • the two power absorption servomotors 90A and 90B are synchronously driven to apply a load to the output shaft To of the FR transmission T.
  • FIG. 25 is an external view of a power absorption durability test apparatus 100G for an FF transmission according to a 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 unit 100 via the torque sensor 172a.
  • the output shaft TRb (TRc) of the FF transmission TR is connected to a power absorption servomotor 90B (90C) via a torque sensor 172b (172c), a pulley portion 180b (180c), and a drive belt.
  • the power absorption servomotor 90B (90C) applies a load to the output shaft TRb (TRc) of the FF transmission TR.
  • the torque sensors 172a, 172b, and 172c have the same configuration as the torque sensors 172a, 172b, and 172c of the seventh embodiment.
  • FIG. 26 is a side view of a torsion test apparatus 3100 according to the thirteenth embodiment of the present invention.
  • the torsion test apparatus 3100 of this embodiment is an apparatus that performs a rotational torsion test of a specimen T1 (for example, a FR vehicle transmission unit) having two rotation shafts.
  • the torsional testing apparatus 3100 rotates the two rotating shafts of the specimen T1 while applying torque by giving a phase difference to the rotation of the two rotating shafts while rotating the two rotating shafts of the specimen T1 synchronously.
  • the torsion test apparatus 3100 of this embodiment includes a control unit C3 that integrally controls the operations of the first drive unit 3110, the second drive unit 3120, and the torsion test apparatus 3100.
  • FIG. 27 is a side view in which a part of the first drive unit 3110 is cut away.
  • 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 speed reducer 3113, a case 3114, a spindle 3115, a chuck device 3116, a torque sensor 3117, a slip ring 3119a, and a brush 3119b.
  • the main body 3110a is disposed horizontally on the top of the base 3110b.
  • the movable plate 3111 is assembled.
  • the servo motor unit 150 is the same as that in the first embodiment.
  • the servo motor unit 150 is fixed on the movable plate 3111 with the output shaft (not shown) oriented in the horizontal direction. Further, the movable plate 3111 of the base 3110b is provided so as to be slidable in the output shaft direction (left and right direction in FIG. 26) of the servo motor unit 150.
  • the output shaft (not shown) of the servo motor unit 150 is connected to the input shaft (not shown) of the speed reducer 3113 by coupling (not shown).
  • An output shaft 3113 a of the speed reducer 3113 is connected to one end of the torque sensor 3117.
  • the other end of the torque sensor 3117 is connected to one end of the spindle 3115.
  • the spindle 3115 is rotatably supported by a bearing 3114a fixed to the frame 3114b of the case 3114.
  • a chuck device 3116 for attaching one end portion (one of the rotating shafts) of the specimen T1 to the first drive portion 3110 is fixed to the other end portion of the spindle 3115.
  • the rotational movement of the output shaft of the servo motor unit 150 is decelerated by the speed reducer 113, and then is applied to one end of the specimen T1 via the torque sensor 3117, the spindle 3115, and the chuck device 3116. It is to be transmitted.
  • a rotary encoder (not shown) for detecting the rotation angle of the spindle 3115 is attached to the spindle 3115.
  • the speed reducer 3113 is fixed to the frame 3114b of the case 3114.
  • the reduction gear 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 a power transmission shaft from the speed reducer 3113 to the chuck device 3116 and also has a function as a device frame that rotatably supports the power transmission shaft at the positions of the speed reducer 3113 and the spindle 3115. That is, the gear mechanism of the speed reducer 3113 to which one end portion of the torque sensor 3117 is connected and the spindle 3115 to which the other end portion of the torque sensor 3117 is connected can freely rotate to the frame 3114b of the case 3114 via a bearing. It is supported.
  • the torque sensor 3117 is not subjected to a bending moment due to the weight of the gear mechanism of the speed reducer 3113 or the spindle 3115 (and the chuck device 3116), and only a test load (torsion load) is applied, so that the test load is detected with high accuracy. can do.
  • a plurality of slip rings 3119a are formed on the cylindrical surface on one end side of the torque sensor 3117.
  • 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 that come into contact with the corresponding slip rings 3119a are attached to the inner periphery of the brush holding frame 3119c.
  • the output signal of the torque sensor 3117 is configured to be output to the slip ring 3119a, and the output signal of the torque sensor 3117 can be taken out of the first drive unit 3110 via the brush 3119b that is in contact with 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. The housing of the specimen T1 is fixed to the support frame S.
  • the torsional testing apparatus 3100 of this embodiment includes an output shaft O and an input shaft I (engine side) of a specimen T1 that is a transmission unit for an FR vehicle, and chuck devices for a first drive unit 3110 and a second drive unit 3120, respectively. While being fixed to 3116 and 3126, the servomotor units 150 and 150 are driven to rotate in synchronization with each other, and the specimen T1 is made to have a difference in the number of rotations (or the phase of rotation) of both chuck devices 3116 and 3126. A torsional load is applied.
  • the chuck device 3126 of the second drive unit 3120 is driven to rotate at a constant speed, and the chuck device 3116 is driven to rotate so that the torque detected by the torque sensor 3117 of the first drive unit 3110 varies according to a predetermined waveform.
  • a periodically varying torque is applied to the specimen T1 which is a transmission unit.
  • the torsion test apparatus 3100 of the present embodiment can precisely drive both the input shaft I and the output shaft O of the transmission unit by the servo motor units 150 and 150, so that the transmission unit is rotationally driven.
  • the test can be performed under conditions close to the actual running state of the automobile.
  • the magnitudes of torque applied to the input shaft I and the output shaft O do not necessarily match. Therefore, in order to grasp the behavior of the specimen T1 during the torsion test more accurately, it is preferable that the torque can be individually measured on the input shaft I side and the output shaft O side.
  • the torque sensor since the torque sensor is provided in both the first drive unit 3110 and the second drive unit 3120 as described above, the input shaft I side and the output shaft O side of the transmission unit (specimen T1). And torque can be measured individually.
  • the input shaft I side of the transmission unit is rotated at a constant speed and torque is applied on the output shaft O side.
  • 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 rotationally driven at a constant speed, and a variable torque is applied to the input shaft I side.
  • both the input shaft I side and the output shaft O side of the transmission unit may be driven to rotate at varying rotational speeds.
  • the torsion test apparatus 3100 of this embodiment can adjust the distance between the chuck apparatuses 3116 and 3126 so as to be compatible with transmission units of various sizes.
  • the movable plate 3111 of the first drive unit 3110 can be moved in the direction of the axis of rotation of the chuck device 3116 (left and right in FIG. 26) with respect to the base 3110b by a movable plate drive mechanism (not shown). ing.
  • the movable plate 3111 is firmly fixed to the base 3110b by a lock mechanism (not shown).
  • the second drive unit 3120 also includes a movable plate drive mechanism similar to the first drive unit 3110.
  • the torsional testing apparatus 3100 performs a rotational torsion test on a transmission unit for an FR vehicle.
  • the present invention is a basic example of the above-described thirteenth embodiment.
  • the present invention is not limited to the configuration, and an apparatus for performing a rotational torsion test of another power transmission mechanism is also included in the present invention.
  • the first, second, and third modifications of the thirteenth embodiment described below are torsion tests suitable for testing transmission units for FF vehicles, differential gear units, and transmission units for 4WD vehicles, respectively. It is a structural example of an apparatus.
  • FIG. 28 is a plan view of a torsion test apparatus 3200 according to a first modification of the thirteenth embodiment of the present invention.
  • the present modification is a configuration example of a torsion test apparatus suitable for the rotational torsion test using the transmission unit for the FF vehicle as the specimen T2.
  • the specimen T2 is a transmission unit incorporating a differential gear, and has an input shaft I, a left output shaft OL, and a right output shaft OR.
  • the torsion test apparatus 3200 of the present modification includes a first drive unit 3210 that drives the input shaft I of the specimen T2, a second drive unit 3220 that drives the left output shaft OL, and a third drive unit that drives the right output shaft OR. 3230.
  • the torsion test apparatus 3200 includes a control unit C3a that integrally controls the operation thereof.
  • the structures of the first drive unit 3210, the second drive unit 3220, and the third drive unit 3230 are all the same as those of the first drive unit 3110 and the second drive unit 3120 according to the basic example of the above-described thirteenth embodiment. Therefore, the description of the overlapping specific configuration is omitted.
  • the input shaft I is driven at a predetermined rotational speed by the first drive unit 3210, and at the same time,
  • 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.
  • a variable torque is applied to each shaft of the transmission unit while rotating the transmission unit. Tests can be performed under conditions close to actual driving conditions.
  • the transmission unit that performs the test using the torsional test apparatus 3200 of the present modification is an apparatus in which the input shaft I, the left output shaft OL, and the right output shaft OR are connected via a gear or the like, and its rotational torsion.
  • the magnitudes of torque applied to the input shaft I, the left output shaft OL, and the right output shaft OR do not match. Further, the torque applied to the left output shaft OL and the right output shaft OR does not always match. Therefore, in order to grasp the behavior of the specimen T2 during the torsion test more accurately, it is preferable that the torque applied to the input shaft I, the left output shaft OL, and the right output shaft OR can be individually measured.
  • the second drive unit 3220 and the third drive unit 3230 may be controlled so that the torque of the left output shaft OL and the torque of the right output shaft OR draw the same waveform.
  • the first drive unit 3210, the second drive unit 3220, and the third drive unit 3230 may be controlled so as to draw a waveform having an opposite phase.
  • 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 so that the speed fluctuates at a constant cycle.
  • all of the input shaft I, the left output shaft OL, and the right output shaft OR may be driven so that the rotation speed varies individually.
  • FIG. 19 is a plan view of a torsion test apparatus 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.
  • 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 the present modification includes a first drive unit 3310 that drives the input shaft I of the specimen T3, a second drive unit 3320 that drives the left output shaft OL, and a third drive unit that drives the right output shaft OR. 3330. Further, the torsion test apparatus 3300 includes a control unit C3b that controls the operation in an integrated manner.
  • the structures of the first drive unit 3310, the second drive unit 3320, and the third drive unit 3330 are the same as those of the first drive unit 3110 and the second drive unit 3120 according to the basic example of the thirteenth embodiment, and thus overlap. A description of the specific configuration is omitted.
  • the torsion test device 3300 When the torsion test device 3300 according to this modification performs a rotational torsion test of the specimen T3, for example, the first drive unit 3310 drives the input shaft I at a predetermined number of revolutions, and at the same time, the second drive unit 320 and the third The drive unit 3330 drives so that torque is applied to the left output shaft OL and the right output shaft OR.
  • the variable torque is applied to each axis of the specimen T3 while rotating each axis of the specimen T3.
  • the test can be performed under conditions close to the actual use state.
  • the differential gear unit is a device in which the input shaft I, the left output shaft OL, and the right output shaft OR are connected via gears.
  • the input shaft I And the magnitude of torque applied to the left output shaft OL and the right output shaft OR do not match. Further, the magnitudes of torque applied to the left output shaft OL and the right output shaft OR do not always match. Therefore, in order to grasp the behavior of the specimen T3 during the test more accurately, it is desirable that the torques of the input shaft I, the left output shaft OL, and the right output shaft OR can be individually measured.
  • the second drive unit 3320 and the third drive unit 3330 may be controlled such that the rotation speed of the input shaft I and the rotation speed of the left output shaft OL and the right output shaft OR draw the same waveform. Further, the second drive unit 3320 and the third drive unit 3330 may be controlled so as to draw different waveforms (for example, such that the speed difference with the input shaft I has an opposite phase).
  • 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 so that the speed fluctuates at a constant period.
  • all of the input shaft I, the left output shaft OL, and the right output shaft OR may be driven so that the rotation speed varies.
  • FIG. 20 is a plan view of a torsion test apparatus 3400 according to a third modification of the thirteenth embodiment of the present invention.
  • a torsion test apparatus 3400 according to this modification is a configuration example of a torsion test apparatus suitable for a rotation torsion test of a specimen T4 having four rotation axes.
  • the specimen T4 is an FF-based electronically controlled 4WD system including a transmission, a front differential gear, a transfer, and an electronically controlled multi-plate clutch not shown.
  • the specimen T4 is connected to an input shaft I connected to the engine, a left output shaft OL and a right output shaft OR connected to left and right front wheel drive shafts, 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 the transmission provided in the specimen T4, and then distributed to the left output shaft OL and the right output shaft OR via the front differential gear. Further, a part of the driving force transmitted to the front differential gear is configured to be branched by transfer and output from the rear output shaft OP.
  • the torsion test apparatus 3400 of the present modification includes a first drive unit 3410 that drives the input shaft I of the specimen T4, a second drive unit 3420 that drives the left output shaft OL, and a third drive unit that drives the right output shaft OR. 3430 and a fourth drive unit 3440 for driving the rear output shaft OP.
  • the torsion test apparatus 3400 includes a control unit C3c that integrally controls the operation thereof.
  • the structures of the first drive unit 3410, the second drive unit 3420, the third drive unit 3430, and the fourth drive unit 3440 are all the same as the first drive unit 3110 and the second drive unit 3120 of the basic example of the thirteenth embodiment. Therefore, the description of the overlapping specific configuration is omitted.
  • the two-axis output servo motor 150A according to the embodiment of the present invention is used in connection with the servo motor 150B having one output shaft.
  • the biaxial output servomotor 150B can be used alone.
  • FIG. 31 is a side view of a torsion test apparatus 4000 according to the fourteenth embodiment of the present invention.
  • the torsion test apparatus 4000 is an apparatus that can perform the rotational torsion test of two specimens T3a and T3b at the same time by using only one two-axis output servo motor 150A.
  • the torsion test apparatus 4000 includes a fixed base 4100, a drive unit 4200, a first reaction force unit 4400A, a second reaction force unit 4400B, and a control unit C4.
  • FIG. 32 is an enlarged view of the drive unit 4200.
  • the drive unit 4200 includes a two-axis output servo motor 150A and a pair of drive transmission units 4200A and 4200B.
  • the biaxial output servomotor 150A is connected to the control unit C4, and the drive is controlled by the control unit C4.
  • the drive transmission units 4200A and 4200B respectively decelerate the rotation of the first output shaft 150A2a and the second output shaft 150A2b of the two-axis output servo motor 150A and transmit them to the input shafts of the specimens T3a and T3b. Since the drive transmission unit 4200A and the drive transmission unit 4200B have the same configuration, details of the configuration will be described only for one drive transmission unit 4200A.
  • the drive transmission unit 4200A includes a frame 4210, a speed reducer 4220, a pulley 4230, a timing belt 4240, a rotary encoder 4250, and a chuck device 4260.
  • the frame 4210 is an angle (L-shaped material) -shaped frame attached on the fixed base 4100, and includes a bottom plate 4212 that is a flat plate disposed horizontally on the fixed base 4100, and a flat plate that stands upright from one end of the upper surface of the bottom plate 4212. And a pair of rib plates 4216 that 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 connected to each other by welding.
  • the vertical plate 4214 is disposed perpendicular to the first output shaft 150A2a of the biaxial output servomotor 150A, and has an opening 4214a formed coaxially with the first output shaft 150A2a.
  • a reduction gear 4220 is inserted into and fixed to the opening 4214a of the vertical plate 4214.
  • the first bracket 150A3 of the two-axis output servo motor 150A is attached to the input side flange plate 4224 of the speed reducer 4220 with a bolt.
  • the first bracket 150A3 is fixed to the input side flange plate 4224 via the reinforcing plate 4212 not only by the mounting seat surface (the right side surface in FIG. 31) but also by a tap hole 150A3t provided on the lower surface thereof.
  • the input side flange plate 4224 of the speed reducer 4220 and the first bracket 150A3 of the two-axis output servo motor 150A are coupled with high rigidity, and a highly accurate test is possible.
  • the first output shaft 150A2a of the two-axis output servomotor 150A is connected to the input shaft (not shown) of the speed reducer 4220. Further, a chuck device 4260 is attached to the tip of the output shaft 4228 of the speed reducer 4220. An input shaft of the specimen T3a is attached to the chuck device 4260. The rotation of the first output shaft 150A2a of the two-axis output servomotor 150A is decelerated by the speed reducer 4220, the torque is amplified, and then transmitted to the input shaft of the specimen T3a via the chuck device 4260.
  • the reduction gear 4220 is provided with an oil supply cup 4222, and the internal space of the reduction gear 4220 is filled with lubricating oil, so that each gear constituting the reduction gear 4220 is always completely immersed in the lubricating oil. Yes.
  • a reciprocating torsional load in the normal range is applied to the specimen, so that the angle at which the specimen is twisted is about several tens of degrees at most, and the amplitude of repeated rotation is one revolution (360 degrees) even on the input shaft of the speed reducer. Often missing.
  • a pulley 4230 is provided on the outer periphery of the output shaft 4228. Further, a rotary encoder 4250 is disposed below the speed reducer 4220 on the vertical plate 4214 of the frame 4210. 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 speed reducer 4220, and the rotation of the output shaft 4228 of the speed reducer 4220 is It is transmitted to the rotary encoder 4250 via the timing belt 4240 and detected. The rotary encoder 4250 is connected to the control unit C4, and a signal indicating the rotation detected by the rotary encoder 4250 is sent to the control unit C4.
  • the first reaction force portion 4400A will be described.
  • the second reaction force portion 4400B has the same configuration as the first reaction force portion 4400A, and thus detailed description thereof is omitted.
  • the first reaction force portion 4400A includes a frame 4410, a torque sensor 4420, a spindle 4440, a bearing portion 4460, and a chuck device 4480.
  • the frame 4410 is an angle (L-shaped material) frame attached to the fixed base 4100 with bolts B, and includes a bottom plate portion 4412 horizontally disposed on the fixed base 4100 and one upper end portion of the bottom plate portion 4412 (see FIG. 31 is provided with a vertical plate 2414 which is a flat plate upright from the left end portion 31) and a pair of rib plates 2416 which are vertically connected to the bottom plate portion 4412 and the vertical plate 2414.
  • the bottom board part 4412, the vertical board 4214, and the rib board 4216 are mutually connected by welding.
  • the bearing portion 4460 is fixed on the bottom plate portion 4412 with bolts B on the drive portion 4200 side of the vertical plate 2414 and the rib plate 2416.
  • the fixed base 4100 includes a first reaction force portion moving mechanism (not shown) that smoothly moves the first reaction force portion 4400A in the direction of the first output shaft 150A2a of the two-axis output servomotor 150A.
  • the first reaction force portion 4400A can be smoothly moved in the direction of the first output shaft 150A2a by operating the first reaction force portion moving mechanism in a state where the bolt B that fixes the top to the fixed base 4100 is loosened.
  • the fixed base 4100 also includes a second reaction force portion moving mechanism (not shown) that smoothly moves the second reaction force portion 4400B in the direction of the second output shaft 150A2b of the two-axis output servomotor 150A.
  • the torque sensor 4420, the spindle 4440, the bearing 4460, and the chuck device 4480 are arranged coaxially with the first output shaft 150A2a of the biaxial output servomotor 150A.
  • One end of the torque sensor 4420 (the left end in FIG. 31) is fixed to the vertical plate 4214 of the frame 4410. Further, one end portion (left end portion in FIG. 31) of the spindle 4440 is fixed to the other end portion of the torque sensor 4420, and a chuck device 4480 is attached to the other end portion of the spindle 4440.
  • An 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 through the chuck device 4480 and the spindle 4440 and detected.
  • the torque sensor 4420 is connected to the control unit C4, and a signal indicating the torque of the output shaft of the specimen T3a detected by the torque sensor 4420 is sent to the control unit C4 and processed.
  • the spindle 4440 is rotatably supported by the bearing portion 4460 in the vicinity of the other end portion (end portion on the chuck device 4480 side). Accordingly, the torque sensor 4420 and the spindle 4440 are both supported by the vertical plate 2414 and the bearing portion 4460, so that a large bending moment is applied to the torque sensor 4420 to prevent an increase in detection error of the torque sensor 4420.
  • the input shaft of the specimen T3a is attached to the chuck device 4260 of the drive transmission unit 4200A, and the chuck device of the first reaction force unit 4400A.
  • the output shaft of the specimen T3a is attached to 4480.
  • the input shaft of the specimen T3b is attached to the chuck device 4260 of the drive transmission unit 4200B, and the output shaft of the specimen T3b is attached to the chuck device 4480 of the second reaction force portion 4400B.
  • the two-axis output servo motor 150A When the two-axis output servo motor 150A is driven in this state, the first output shaft 150A2a and the second output shaft 150A2b rotate in the same phase, and the chuck devices 4260 of the drive transmission unit 4200A and the drive transmission unit 4200B also rotate in the same phase. . Thereby, the same torsion amount is added to the specimens T3a and T3b, that is, the torsion test under the same conditions is performed on the specimens T3a and T3b.
  • the torsion test (fatigue test) of the two specimens T3a and T3b can be performed simultaneously using one servo motor and the control unit C4. It becomes possible to perform a test.
  • 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 of a linear motion actuator in combination with a linear motion transducer such as a feed screw mechanism.
  • a linear motion actuator for example, a vibration test apparatus or a tension / compression test apparatus can be realized.
  • FIG. 33 is a top view of a vibration test apparatus (vibration apparatus) 5000 according to the fifteenth embodiment of the present invention.
  • the vibration test apparatus 5000 fixes a workpiece to be subjected to a vibration test on a table 5100, and uses the first, second, and third actuators 5200, 5300, and 5400, and the workpiece on the table 5100. Is vibrated in three orthogonal directions.
  • the direction in which the first actuator 5200 vibrates the table 5100 (the vertical direction in FIG. 33) is the X-axis direction
  • the direction in which the second actuator 5300 vibrates the table 5100 (the horizontal direction in FIG. 33).
  • the direction in which the third actuator 5400 vibrates the table that is, the vertical direction (the direction perpendicular to the paper surface in FIG. 33) is defined as the Z-axis direction.
  • FIG. 38 is a block diagram of a control system for a vibration test apparatus according to an embodiment of the present invention.
  • the first, second, and third actuators 5200, 5300, and 5400 are provided with vibration sensors 5220, 5320, and 5420, respectively.
  • the control unit C5 feedback-controls the first, second, and third actuators 5200, 5300, and 5400 (specifically, the servo motor units 150X, 150Y, and 150Z) based on the outputs of these vibration sensors, and thereby the desired
  • the table 5100 and the workpiece mounted on it can be vibrated at an amplitude and frequency (these parameters are usually set as a function of time).
  • the servo motor units 150X, 150Y, and 150Z are the same as the servo motor unit 150 of the first embodiment.
  • the first, second, and third actuators 5200, 5300, and 5400 are configured such that a motor, a power transmission member, and the like are mounted on base plates 5202, 5302, and 5402, respectively.
  • the base plates 5202, 5302, and 5402 are fixed on the apparatus base 5002 with bolts (not shown).
  • adjusters A are arranged at a plurality of positions close to the base plates 5202, 5302, and 5402.
  • the adjuster A has a female screw portion A1 fixed to the apparatus base 5002 with a bolt AB, and a male screw portion A2 screwed into the female screw portion A1.
  • the male screw portion A2 is a columnar member having a thread formed on a cylindrical surface, and the male screw portion A2 is engaged with a screw hole formed in the female screw portion A1 and rotated to thereby rotate the male screw.
  • the part A2 can be advanced and retracted relative to the corresponding base plate.
  • One end portion of the male screw portion A2 (side that is proximal to the corresponding base plate) is formed in a substantially spherical shape, and the base plate is brought into contact with the side surface of the corresponding base plate by contacting the protruding portion with the side surface of the corresponding base plate. Fine adjustment of the position can be performed. Further, a hexagon socket for a hexagon wrench (not shown) is formed at the other end of the external thread A2 (on the side that is distal to the corresponding base plate). .
  • the nut A3 is attached to the male screw portion A2 so that the male screw portion A2 is not loosened by vibration or the like that can be transmitted from the base plate to the adjuster A by a vibration test. Yes.
  • the nut A3 is attached so that one end surface thereof is in contact with the female screw portion A1, and from this state, the nut A3 is screwed in and the female screw portion A1 is pushed in, and an axial force is applied to the male screw portion A2 and the female screw portion A1.
  • the axial force prevents the female thread A1 from loosening from the female thread A2 by the frictional force generated in the thread of the female thread A2 and the female thread A1.
  • FIG. 34 is a side view of the first actuator 5200 according to the embodiment of the present invention as 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.
  • FIG. 35 is a partially cutaway top view of the first actuator 5200 showing the internal structure.
  • X axis positive direction the direction along the X axis from the first actuator 5200 toward the table 5100
  • X axis the direction along the X axis from the table 5100 toward the first actuator
  • a frame 5222 made up of a plurality of beams 5222a and a top plate 5222b welded to each other is fixed by welding.
  • the bottom plate 5242 of the support mechanism 5240 for supporting the driving mechanism 5210 for exciting the table 5100 (FIG. 33) and the connecting mechanism 5230 for transmitting the excitation motion by the driving mechanism 5210 to the table 5100 is a frame. It is fixed on a top plate 5222b of 5222 via a bolt (not shown).
  • the drive mechanism 5210 includes a servo motor unit 150X, a coupling 5260, a bearing 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.
  • the bearing portion 5216 is supported by a bearing support plate 5244 fixed by welding perpendicularly to the bottom plate 5242 of the support mechanism 5240, and rotatably supports the ball screw 5218.
  • the ball nut 5219 engages with the ball screw 5218 while being supported by the bearing support plate 5244 so as not to move around its axis.
  • the ball screw rotates and the ball nut 5219 advances and retreats in the axial direction (that is, the X-axis direction).
  • the movement of the ball nut 5219 is transmitted to the table 5100 via the coupling mechanism 5230, whereby the table 5100 is driven in the X-axis direction.
  • the table 5100 can be vibrated in the X-axis direction with a desired amplitude and cycle.
  • the motor support plate 5246 is welded perpendicularly to the bottom plate 5242 on the upper surface of the bottom plate 5242 of the support mechanism 5240.
  • the servo motor unit 150X is cantilevered on one surface of the motor support plate 5246 (the surface on the X axis negative direction side) 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 surface side of 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.
  • a rib 5248 is provided between the bottom plate 5242 and the motor support plate 5246.
  • the bearing portion 5216 has a pair of angular ball bearings 5216a and 5216b (5216a on the X axis negative direction side and 5216b on the X axis positive direction side) combined in front combination. is doing.
  • Angular ball bearings 5216 a and 5216 b are housed in the hollow portion of bearing support plate 5244.
  • a bearing pressing plate 5216c is provided on one surface (surface in the positive X-axis direction) of the angular ball bearing 5216b. By fixing the bearing pressing plate 5216c to the bearing support plate 5244 using a bolt 5216d, Angular ball bearing 5216b is pushed in the negative direction of the X-axis.
  • a screw portion 5218a is formed on a cylindrical surface adjacent to the bearing portion 5216 on the X-axis negative direction side.
  • a collar 5217 having a female screw formed on the inner periphery is attached to the screw portion 5218.
  • 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. is doing.
  • the nut guide 5232 is fixed to the ball nut 5219.
  • the pair of Y-axis rails 5234 are both rails extending in the Y-axis direction, and are fixed side by side in the vertical direction at the end of the nut guide 5232 on the X-axis positive direction side.
  • the pair of Z-axis rails 5235 are rails extending in the Z-axis direction, and are fixed to the end of the table 5100 on the X-axis negative direction side by side in the Y-axis direction.
  • the intermediate stage 5231 has a Y-axis runner block 5231a that engages with each of the Y-axis rails 5234 on the surface on the negative side of the X-axis, and a Z-axis runner block 5231b that engages with each of the Z-axis rails 5235 on the X-axis. It is a block provided on the surface on the positive direction side, and is configured to be slidable with respect to both the Y-axis rail 5234 and the Z-axis rail 5235.
  • the intermediate stage 5231 can slide in the Z-axis direction with respect to the table 5100 and can slide in the Y-axis direction with respect to the nut guide 5232. Therefore, the nut guide 5231 can slide in the Y-axis direction and the Z-axis direction with respect to the table 5100. For this reason, even if the table 5100 is vibrated in the Y-axis direction and / or the Z-axis direction by another actuator 5300 and / or 5400, the nut guide 5232 is not displaced thereby. That is, bending stress resulting from displacement in the Y-axis direction and / or Z-axis direction of the table 5100 is not applied to the ball screw 5218, the bearing 5216, the coupling 5260, or the like.
  • the pair of X-axis rails 5237 are both rails extending in the X-axis direction, and are arranged and fixed on the bottom plate 5242 of the support mechanism 5240 in the Y-axis direction.
  • the X-axis runner block 5233 engages with each of the X-axis rails 5237 and is slidable along the X-axis rails 5237.
  • the runner block mounting member 5238 is a member fixed to the bottom surface of the nut guide 5232 so as to protrude toward both sides in the Y-axis direction, and the X-axis runner block 5233 is fixed to the bottom of the runner block mounting member 5238.
  • the nut guide 5232 is guided by the X-axis rail 5237 via the runner block mounting member 5238 and the X-axis runner block 5233, and can be moved only in the X-axis direction.
  • the moving direction of the nut guide 5232 is limited to only the X-axis direction, when the servo motor unit 150X is driven to rotate the ball screw 5218, the nut guide 5232 and the nut guide 5232 are engaged.
  • the table 5100 that moves forwards and backwards in the X-axis direction.
  • Position detection means 5250 is disposed on one side surface (the front side in FIG. 34, the right side in FIG. 35) 5238a of the runner block mounting member 5238.
  • 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 sensor 5251. have.
  • the proximity sensor 5251 is an element that can detect whether any object is in proximity (for example, within 1 millimeter) in front of each proximity sensor.
  • the proximity sensor 5251 can detect whether or not there is a detection plate 5252 in front of each proximity sensor 5251.
  • the control unit C5 of the vibration test apparatus 5000 can perform feedback control of the servo motor unit 150X using, for example, the detection result of the proximity sensor 5251 (FIG. 38).
  • a restriction block 5236 is provided so as to sandwich the X-axis runner block 5233 from both sides in the X-axis direction.
  • the restriction block 5236 is for limiting the movement range of the nut guide 5232. That is, when the servo motor unit 150X is driven and the nut guide 5232 is continuously moved in the positive direction of the X axis, finally, the restriction block 5236 and the runner block mounting member disposed on the positive side of the X axis. 5238 is in contact with the nut guide 5232, and the nut guide 5232 cannot move further in the positive direction of the X axis.
  • the first actuator 5200 and the second actuator 5300 described above have the same structure except that the installation directions are different (the X axis and the Y axis are interchanged). Therefore, detailed description of the second actuator 5300 is omitted.
  • FIG. 36 is a side view of the table 5100 and the third actuator 5400 as viewed from the X-axis direction (from the bottom to the top in FIG. 16). This side view is also partially cut away to show the internal structure.
  • FIG. 37 is a side view of the table 5100 and the third actuator 5400 according to the embodiment of the present invention viewed from the Y-axis direction (from the left side to the right side in FIG. 33). FIG. 37 is also partially cut away to show the internal structure.
  • the direction along the Y axis from the second actuator 5300 toward the table 5100 is the Y axis positive direction
  • the direction along the Y axis from the table 5100 toward the second actuator 5300 is the Y axis negative. Defined as direction.
  • a frame 5422 is provided on the base plate 5402.
  • the frame 5422 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 has been.
  • Each beam 5422a is welded at its lower end to the upper surface of the base plate 5402 and at its upper end to the lower surface of the top plate 5422b.
  • the bearing support plate 5442 of the support mechanism 5440 is fixed on the top plate 5422b of the frame 5422 via a bolt (not shown).
  • This bearing support plate 5442 is a member for supporting a drive mechanism 5410 for vibrating the table 5100 (FIG. 33) in the vertical direction and a 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.
  • the coupling 5460 connects the drive shaft 152Z of the servo motor unit 150Z and the ball screw 5418.
  • the bearing portion 5416 is fixed to the bearing support plate 5442 described above, and supports the ball screw 5418 to be rotatable.
  • the ball nut 5419 engages with the ball screw 5418 while being supported by the bearing support plate 5442 so as not to move around its axis. Therefore, when the servo motor unit 150Z is driven, the ball screw rotates, and the ball nut 5419 advances and retreats in the axial direction (that is, the Z-axis direction).
  • the movement of the ball nut 5419 is transmitted to the table 5100 via the coupling mechanism 5430, so that the table 5100 is driven in the Z-axis direction. Then, by controlling the servo motor unit 150Z so as to switch the rotation direction of the servo motor unit 150Z with a short cycle, 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 connection plates 5443.
  • a servo motor unit 150Z is suspended and fixed on the lower surface of the motor support plate 5446.
  • the motor support plate 5446 is provided with an opening 446a.
  • 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.
  • the apparatus base 5002 is provided with a cavity 5002a for accommodating the servo motor unit 150Z.
  • the base plate 5402 is provided with an opening 5402a through which the servo motor unit 150Z is passed.
  • the bearing portion 5416 is provided so as to penetrate the bearing support plate 5442.
  • the structure of the bearing portion 5416 is the same as that of the bearing portion 5216 (FIGS. 34 and 35) in the first actuator 5200, and a detailed description thereof will be omitted.
  • 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. Yes.
  • the movable frame 5432 includes a frame portion 5432a fixed to the ball nut 5419, a top plate 5432b fixed to the upper end of the frame portion 5432a, and a side wall 5432c fixed so as to extend downward from both edges of the top plate 5432b in the X-axis direction.
  • the pair of Y-axis rails 5435 are both rails extending in the Y-axis direction, and are fixed on the upper surface of the top plate 5432b of the movable frame 5432 in the X-axis direction.
  • the pair of X-axis rails 5434 are rails that 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 upper part, and a Y-axis runner block 5431b that engages with each of the Y-axis rails 5435 is provided at the lower part.
  • the rail 5434 and the Y-axis rail 435 are configured to be slidable.
  • One intermediate stage 5431 is provided for 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 rail 5434 and the Y-axis rail 5435 intersect at four points. Therefore, in the present embodiment, four intermediate stages 5431 are used.
  • each of the intermediate stages 5431 can slide in the X-axis direction with respect to the table 5100 and can slide in the Y-axis direction with respect to the movable frame 5432. That is, the movable frame 5432 can slide in the X-axis direction and the Y-axis direction with respect to the table 5100. For this reason, even if the table 5100 is vibrated in the X-axis direction and / or the Y-axis direction by another actuator 5200 and / or 5300, the movable frame 5432 is not displaced thereby. That is, bending stress due to displacement of the table 5100 in the X-axis direction and / or Y-axis direction is not applied to the ball screw 5418, the bearing 5416, the coupling 5460, or the like.
  • the movable frame 5432 supports a relatively heavy table 5100 and a workpiece, so that the distance between the X-axis rail 5434 and the Y-axis rail 5435 is set to be the Y-axis rail 5234 and Z It is wider than the shaft rail 5235. Therefore, when the table 5100 and the movable frame 5432 are connected by only one intermediate stage as in the first actuator 5200, the intermediate stage becomes large and the load applied to the movable frame 5432 increases.
  • the two pairs of Z-axis rails 5437 are rails extending in the Z-axis direction, and are fixed to the side walls 5432c of the movable frame 5432 in pairs in the Y-axis direction.
  • the Z-axis runner block 5433 engages with each of the Z-axis rails 5437 and can slide along the Z-axis rails 5437.
  • the Z-axis runner block 5433 is fixed to the upper surface of the top plate 5422b of the frame 5422 via a runner block mounting member 5438.
  • the runner block mounting member 5438 has a side plate 5438a disposed substantially parallel to the side wall 5432c of the movable frame 5432, and a bottom plate 5438b fixed to the lower end of the side plate 5438a. It has become.
  • the runner block mounting member 5438 is reinforced by ribs so as to withstand this rotational moment.
  • a pair of first ribs 5438c are provided at 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 further, a gap is provided between the pair of first ribs 5438c.
  • a second rib 5438d is provided.
  • the Z-axis runner block 5433 is fixed to the frame 5422 and is slidable with respect to the Z-axis rail 5437. Therefore, the movable frame 5432 is slidable in the vertical direction, and movement of the movable frame 5432 in other directions is restricted. Thus, since the moving direction of the movable frame 5432 is limited only in the vertical direction, when the servo motor unit 150Z is driven to rotate the ball screw 5418, the movable frame 5432 and the movable frame 5432 are engaged. The table 5100 moves back and forth in the vertical direction.
  • the third actuator 5400 is provided with 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 test 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).
  • two pairs of rails and an intermediate stage configured to be slidable with respect to the rails are provided between the actuators and the table 5100 whose drive axes are orthogonal to each other. Yes.
  • the table 5100 can slide in any direction on a plane perpendicular to the driving direction of the actuator. For this reason, even if the table 5100 is displaced by a certain actuator, the load or moment resulting from this displacement is not applied to the other actuator, and the other actuator and the table 5100 are engaged 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. For this reason, in the present embodiment, the three actuators 5200, 5300, and 5400 can be simultaneously driven to vibrate the table 5100 and the workpiece fixed thereon in three axial directions.
  • a connecting portion including a guide mechanism in which a rail and a runner block are combined is provided between the actuators 5200, 5300, and 5400 and the table 5100.
  • a similar guide mechanism is provided in the actuators 5200, 5300, and 5400, and this guide mechanism is used to guide the nut of the ball screw mechanism of each actuator.
  • an ultra-low inertia servo motor is used for the torque generator, but the configuration of the present invention is not limited to this.
  • a configuration using another type of electric motor for example, an inverter motor
  • an encoder is provided in the motor and feedback control is performed based on the rotation state (for example, the rotation speed or angular position) of the output shaft of the motor detected by the encoder.
  • the above embodiment is an example in which the present invention is applied mainly to an endurance test device for a power transmission device for automobiles.
  • the present invention is not limited to this and is used for various applications in the entire industry. Can do.
  • the present invention can be used to evaluate the mechanical characteristics and durability of a motorcycle, an agricultural machine, a construction machine, a railway vehicle, a ship, an aircraft, a power generation system, a water supply / drainage system, or various components constituting them. it can.
  • one servo motor 150B (having one output shaft) and one two-axis output servo motor 150A are connected in two stages.
  • 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 be used.

Landscapes

  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
  • Tires In General (AREA)
  • Motor Or Generator Frames (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Apparatuses For Generation Of Mechanical Vibrations (AREA)
  • Investigating Strength Of Materials By Application Of Mechanical Stress (AREA)
  • Force Measurement Appropriate To Specific Purposes (AREA)

Abstract

L'invention concerne un moteur à deux arbres secondaires comprenant : un châssis principal cylindrique ; un premier support sensiblement du type plaque qui est fixé à une extrémité axiale du châssis principal ; un second support sensiblement du type plaque qui est fixé à l'autre extrémité axiale du châssis principal ; et un arbre d'entraînement qui passe à travers la partie creuse du châssis principal, pénètre à travers le premier support et le second support, et est supporté de manière rotative par des roulements prévus dans le premier support et le second support. Une extrémité de l'arbre d'entraînement fait saillie vers l'extérieur à partir du premier support et forme un premier arbre secondaire pour transmettre une force d'entraînement à l'extérieur, et l'autre extrémité de l'arbre d'entraînement fait saillie vers l'extérieur à partir du second support et forme un second arbre secondaire pour transmettre la force d'entraînement à l'extérieur.
PCT/JP2013/077747 2012-10-12 2013-10-11 Moteur à deux arbres secondaires, unité moteur, simulateur d'alimentation, dispositif de test de torsion, dispositif de test de torsion de rotation, dispositif de test de pneu, actionneur linéaire et dispositif à vibrations WO2014058051A1 (fr)

Priority Applications (7)

Application Number Priority Date Filing Date Title
CN201380053483.5A CN104737423B (zh) 2012-10-12 2013-10-11 双轴输出马达、马达单元、动力模拟器、扭转测试装置、旋转扭转测试装置、轮胎测试装置、线性致动器和振动装置
CN201810402131.0A CN108663147B (zh) 2012-10-12 2013-10-11 转矩赋予单元、驱动装置和轮胎测试装置
KR1020207008237A KR102190139B1 (ko) 2012-10-12 2013-10-11 하중 부여부, 구동 시스템, 기계 시험 장치, 동력 시뮬레이터 및 타이어 시험 장치
JP2014540905A JP5986640B2 (ja) 2012-10-12 2013-10-11 モータユニット、動力シミュレータ、ねじり試験装置、回転ねじり試験装置、直動アクチュエータ及び加振装置
KR1020187019525A KR102079593B1 (ko) 2012-10-12 2013-10-11 타이어 시험 장치
KR1020207008240A KR102190153B1 (ko) 2012-10-12 2013-10-11 비틀림 시험 장치
KR1020157012083A KR102093861B1 (ko) 2012-10-12 2013-10-11 모터 유닛, 회전 비틀림 시험 장치, 비틀림 시험 장치, 직동 액추에이터, 가진 장치 및 동력 시뮬레이터

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
JP2012226487 2012-10-12
JP2012-226487 2012-10-12
JP2012-270822 2012-12-11
JP2012-270821 2012-12-11
JP2012270822 2012-12-11
JP2012270821 2012-12-11
JP2013-180798 2013-08-31
JP2013180798 2013-08-31

Publications (1)

Publication Number Publication Date
WO2014058051A1 true WO2014058051A1 (fr) 2014-04-17

Family

ID=50477513

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/JP2013/077747 WO2014058051A1 (fr) 2012-10-12 2013-10-11 Moteur à deux arbres secondaires, unité moteur, simulateur d'alimentation, dispositif de test de torsion, dispositif de test de torsion de rotation, dispositif de test de pneu, actionneur linéaire et dispositif à vibrations

Country Status (5)

Country Link
JP (8) JP5986640B2 (fr)
KR (4) KR102093861B1 (fr)
CN (3) CN108663147B (fr)
TW (3) TWI697179B (fr)
WO (1) WO2014058051A1 (fr)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105043757A (zh) * 2015-05-31 2015-11-11 吉林大学 电力开环吊挂式传动***可靠性试验台
CN106527354A (zh) * 2016-12-21 2017-03-22 华南理工大学 基于拉压力传感器反馈的双轴同步运动控制装置及方法
CN106596024A (zh) * 2016-12-25 2017-04-26 山西汾西重工有限责任公司 航行器推进段的振动测量装置及振动测量方法
CN108183578A (zh) * 2018-03-27 2018-06-19 河南凌翼智联装备有限公司 双子式同轴伺服驱动装置
CN108444730A (zh) * 2018-03-29 2018-08-24 中国汽车技术研究中心有限公司 一种商用车气压制动器扭转疲劳测试***
WO2019026733A1 (fr) * 2017-08-03 2019-02-07 国際計測器株式会社 Procédé de test de pneu, dispositif de test de pneu et dispositif de dispersion
CN109520733A (zh) * 2019-01-05 2019-03-26 中国船舶重工集团公司第七0三研究所 一种永磁联轴器的加载试验装置
CN109870360A (zh) * 2019-03-18 2019-06-11 吉林大学 一种曲轴可靠性试验装置
ES2728422A1 (es) * 2018-04-23 2019-10-24 Jaroslav Rehak Motor eléctrico girando sobre el eje de rotación
KR20200028429A (ko) * 2017-07-10 2020-03-16 디-박스 테크놀러지스 인코포레이트 모션 시뮬레이터를 위한 리니어 액츄에이터
CN111076926A (zh) * 2019-12-12 2020-04-28 吉林大学 数控刀架三联齿盘可靠性试验台
CN113607408A (zh) * 2021-06-15 2021-11-05 金华卓远实业有限公司 一种中置电机齿轮测试机
WO2021225133A1 (fr) * 2020-05-08 2021-11-11 国際計測器株式会社 Dispositif d'essai de roue
CN113843691A (zh) * 2021-11-15 2021-12-28 周梅 一种机箱模具加工磨床
US11519387B2 (en) * 2017-06-30 2022-12-06 Agile Wind Power Ag Vertical wind turbine comprising rotor blade-supporting pitch motor, as well as kit for same, and method for operating same

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016024340A1 (fr) * 2014-08-12 2016-02-18 株式会社ハーモニック・ドライブ・システムズ Actionneur rotatif
JP6673739B2 (ja) * 2016-04-15 2020-03-25 株式会社神戸製鋼所 タイヤの転がり抵抗の評価装置及び評価方法
SE540015C2 (en) 2016-10-17 2018-02-27 Husqvarna Ab Safety arrangement and method for a floor surfacing machine
DE102016224138A1 (de) * 2016-12-05 2018-06-07 Zf Friedrichshafen Ag Elektromotor für eine Antriebseinheit eines Antriebsstrangprüfstands
CN106769520B (zh) * 2017-01-23 2024-01-23 上海市质量监督检验技术研究院 一种餐饮具负重试验机
WO2018159199A1 (fr) 2017-02-28 2018-09-07 国際計測器株式会社 Appareil de test de simulation de collision et appareil de test d'impact
CN107063610B (zh) * 2017-06-02 2023-07-21 南方英特空调有限公司 一种四轴电磁扭振综合测试平台
CN107104533B (zh) * 2017-06-15 2024-06-07 湖南方略环保技术有限公司 一种机电装置及具有该机电装置的制样设备
JP6699955B2 (ja) * 2017-06-21 2020-05-27 株式会社ハーモニック・ドライブ・システムズ 回転アクチュエータおよび直動アクチュエータ
DE112018005472T5 (de) * 2017-09-29 2020-06-25 Sintokogio, Ltd. Zahnradpositioniervorrichtung, Spannungsmesssystem, Zahnradpositionierverfahren und Beanspruchungs-Messverfahren
JP2020102939A (ja) * 2018-12-21 2020-07-02 日本電産株式会社 アクチュエータ
TWI700420B (zh) * 2019-04-19 2020-08-01 楊紫菱 高壓處理機的具有飛輪的動力驅動裝置及使用其之高壓處理機
CN110033557A (zh) * 2019-05-05 2019-07-19 东莞市势为物联网科技有限公司 一种取货模组
CN110048543A (zh) * 2019-05-23 2019-07-23 樊泽洲 无虚位电机模组
JP7166644B2 (ja) * 2020-04-28 2022-11-08 株式会社ニューギン 遊技機
CN111654152A (zh) * 2020-06-15 2020-09-11 博雅工道（北京）机器人科技有限公司 单驱动双轴电机及机械臂
RU2745673C1 (ru) * 2020-07-16 2021-03-30 Публичное акционерное общество "Транснефть" (ПАО "Транснефть") Нагнетатель для испытаний элементов рабочего колеса безвального насоса
CN112197924A (zh) * 2020-09-27 2021-01-08 脉创测控装备科技（苏州）有限公司 透平机叶片高低周疲劳测试***
CN113644780B (zh) * 2021-07-28 2022-06-10 智新科技股份有限公司 一种电机定位装置
TWI788248B (zh) * 2022-03-30 2022-12-21 東佑達自動化科技股份有限公司 具有傳動皮帶的電動機裝置

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03200043A (ja) * 1989-12-28 1991-09-02 Saginomiya Seisakusho Inc 回転捩り試験機における捩り角度検出装置
JPH05126207A (ja) * 1991-10-30 1993-05-21 Toyota Autom Loom Works Ltd 振動体の防振構造
JP3007926U (ja) * 1994-08-18 1995-02-28 多摩川精機株式会社 中空軸モータ
JPH11150927A (ja) * 1997-11-19 1999-06-02 Ckd Corp 出力装置
JP2000193574A (ja) * 1998-12-24 2000-07-14 Shimadzu Corp 回転体用ねじり試験機
JP2003125554A (ja) * 2001-10-11 2003-04-25 Kss Kk リニアアクチュエータ
WO2008133187A1 (fr) * 2007-04-19 2008-11-06 Kokusai Keisokuki Kabushiki Kaisha Dispositif de test polyvalent, actionneur linéaire et dispositif d'essai de torsion
JP2008267939A (ja) * 2007-04-19 2008-11-06 Kokusai Keisokki Kk ねじり試験装置

Family Cites Families (53)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS529881B2 (fr) * 1973-09-26 1977-03-19
JPS53140482U (fr) * 1977-04-13 1978-11-07
JPS5475701A (en) * 1977-11-25 1979-06-16 Fuji Heavy Ind Ltd Power circulating type power train endurance tester
US4238954A (en) * 1979-02-23 1980-12-16 Mts Systems Corporation Flat belt tire tester
JPS5791440A (en) * 1980-11-28 1982-06-07 Kobe Steel Ltd Tire tester
JPS58101157U (ja) * 1981-12-28 1983-07-09 東洋ゴム工業株式会社 駆動制動特性試験機
JPS58163243A (ja) * 1982-03-19 1983-09-28 Seiko Instr & Electronics Ltd 小型偏平モ−タ
JPS5970940A (ja) * 1982-10-15 1984-04-21 Mitsubishi Heavy Ind Ltd タイヤ試験装置
JPS6242029A (ja) * 1986-08-13 1987-02-24 Kobe Steel Ltd タイヤ試験機
JPH03284137A (ja) * 1990-03-29 1991-12-13 Nippon Mini Motor Kk モータの取付構造
JPH04128771A (ja) * 1990-09-19 1992-04-30 Hitachi Ltd ドラム駆動装置と回転ドラム及びこれを用いた記録装置
JP3007926B2 (ja) 1990-11-15 2000-02-14 オムロン株式会社 データキャリア及び識別システム
JPH0793862B2 (ja) * 1991-07-16 1995-10-11 リンコ・ジャパン株式会社 ブレストプロセッサー
JP2558361Y2 (ja) * 1991-11-06 1997-12-24 株式会社明電舎 トルク検出器
JPH0742668B2 (ja) * 1992-11-17 1995-05-10 宮崎鉄工株式会社 撚線機
JPH06288870A (ja) * 1993-03-31 1994-10-18 Shinko Electric Co Ltd ねじり加振装置
JPH07245912A (ja) * 1994-01-17 1995-09-19 Fuji Electric Co Ltd 回転界磁形同期電動機駆動巻揚機
JP3398205B2 (ja) * 1994-02-21 2003-04-21 国際計測器株式会社 一歯面噛合式歯車試験による歯面の打痕検出方法
JPH0847211A (ja) * 1994-07-29 1996-02-16 Toyota Motor Corp モータの試験装置
JPH09140094A (ja) * 1995-11-17 1997-05-27 Toyota Motor Corp 回転駆動源
JPH09285081A (ja) * 1996-04-10 1997-10-31 Toyota Autom Loom Works Ltd 多軸モータ
TW351027B (en) * 1996-04-22 1999-01-21 Seiko Epson Corp Small motor and the motor drive
JPH1078361A (ja) * 1996-09-02 1998-03-24 Sony Corp 回転トルクチェック装置
JP2002078289A (ja) * 2000-08-31 2002-03-15 Nidec-Shimpo Corp 回転駆動装置
TW452030U (en) * 2001-01-30 2001-08-21 Lee Yi Ho Auxiliary power motor
US6584877B1 (en) * 2001-05-07 2003-07-01 Akron Special Machinery, Inc. Tire uniformity machine drive assembly
JP4552353B2 (ja) * 2001-05-11 2010-09-29 ソニー株式会社 サーボ・アクチュエータ並びにその位置検出装置
JP3887677B2 (ja) * 2002-10-01 2007-02-28 Ｎｔｎ株式会社 車軸装置端部荷重負荷試験機
DE10324664A1 (de) 2003-05-30 2004-12-30 Siemens Ag Rollen und Rollenmotoren
JP4339048B2 (ja) * 2003-08-25 2009-10-07 国際計測器株式会社 タイヤのユニフォーミティ計測方法及び装置、並びにタイヤ修正方法及び装置
DE102004055306B4 (de) * 2003-11-21 2007-06-14 Smc K.K. Stellglied
JP2006072621A (ja) * 2004-09-01 2006-03-16 Bridgestone Corp 回転角度検出システム
JP4747754B2 (ja) 2005-09-16 2011-08-17 日本電産株式会社 モータ
JP2008082709A (ja) * 2006-09-25 2008-04-10 Sumitomo Rubber Ind Ltd タイヤ性能測定装置およびレース用タイヤの性能測定方法
JP2008174190A (ja) 2007-01-22 2008-07-31 Mitsuba Corp パーキングロック装置の電動アクチュエータ
JP5073352B2 (ja) * 2007-04-13 2012-11-14 東芝機械株式会社 モータユニット
JP4902607B2 (ja) * 2007-08-24 2012-03-21 国際計測器株式会社 直動アクチュエータ
RU2353945C1 (ru) * 2007-09-19 2009-04-27 ЗАО "Завод по ремонту электроподвижного состава" Универсальная установка для проверки электродвигателей
JP4310365B1 (ja) * 2008-02-26 2009-08-05 株式会社神戸製鋼所 タイヤ試験機及びタイヤの試験方法
CN101521444A (zh) * 2008-03-01 2009-09-02 高明真 一种高起动品质因数电机及其起动方法
JP5226398B2 (ja) * 2008-06-20 2013-07-03 株式会社神戸製鋼所 タイヤ試験装置、これに用いられるタイヤ装着軸及びタイヤ試験方法
US8250915B1 (en) * 2008-07-03 2012-08-28 Hunter Engineering Company Tire changer with actuated load roller
JP5179999B2 (ja) * 2008-08-12 2013-04-10 株式会社神戸製鋼所 タイヤ試験機の駆動制御方法及びタイヤ試験機
CN201302606Y (zh) * 2008-10-31 2009-09-02 北京理工大学 伺服***复杂负载工况模拟和性能测试装置
CN201444600U (zh) * 2009-06-24 2010-04-28 于忠 一种外壳旋转式电动机
NL2003350C2 (nl) * 2009-08-13 2011-02-15 Vmi Holland Bv Bandenbouwtrommel voor het bouwen van een ongevulkaniseerde band.
JP5558219B2 (ja) * 2010-06-16 2014-07-23 東京パーツ工業株式会社 モータアクチュエータ
JP2012078318A (ja) * 2010-10-06 2012-04-19 Ono Sokki Co Ltd タイヤ試験装置
RU2554048C2 (ru) * 2010-12-16 2015-06-20 Баумюллер Нюрнберг Гмбх Электрическая машина, в частности насосный агрегат
CN102162780B (zh) * 2010-12-20 2013-03-20 长春设备工艺研究所 扭力轴数控强力扭转测试试验台
CN102684380A (zh) * 2011-03-10 2012-09-19 湖南华强电气有限公司 汽车空调用电动压缩机的发电机机构
TWM418287U (en) * 2011-08-11 2011-12-11 Innova Rubber Co Ltd Detent simulation mechanism of wheel testing machine
CN102359883B (zh) * 2011-08-19 2013-05-15 安徽和均自动化装备有限公司 汽车传动部件自动同轴试验测试用驱动机构

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH03200043A (ja) * 1989-12-28 1991-09-02 Saginomiya Seisakusho Inc 回転捩り試験機における捩り角度検出装置
JPH05126207A (ja) * 1991-10-30 1993-05-21 Toyota Autom Loom Works Ltd 振動体の防振構造
JP3007926U (ja) * 1994-08-18 1995-02-28 多摩川精機株式会社 中空軸モータ
JPH11150927A (ja) * 1997-11-19 1999-06-02 Ckd Corp 出力装置
JP2000193574A (ja) * 1998-12-24 2000-07-14 Shimadzu Corp 回転体用ねじり試験機
JP2003125554A (ja) * 2001-10-11 2003-04-25 Kss Kk リニアアクチュエータ
WO2008133187A1 (fr) * 2007-04-19 2008-11-06 Kokusai Keisokuki Kabushiki Kaisha Dispositif de test polyvalent, actionneur linéaire et dispositif d'essai de torsion
JP2008267939A (ja) * 2007-04-19 2008-11-06 Kokusai Keisokki Kk ねじり試験装置

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105043757A (zh) * 2015-05-31 2015-11-11 吉林大学 电力开环吊挂式传动***可靠性试验台
CN106527354A (zh) * 2016-12-21 2017-03-22 华南理工大学 基于拉压力传感器反馈的双轴同步运动控制装置及方法
CN106527354B (zh) * 2016-12-21 2023-03-21 华南理工大学 基于拉压力传感器反馈的双轴同步运动控制装置及方法
CN106596024A (zh) * 2016-12-25 2017-04-26 山西汾西重工有限责任公司 航行器推进段的振动测量装置及振动测量方法
US11519387B2 (en) * 2017-06-30 2022-12-06 Agile Wind Power Ag Vertical wind turbine comprising rotor blade-supporting pitch motor, as well as kit for same, and method for operating same
KR20200028429A (ko) * 2017-07-10 2020-03-16 디-박스 테크놀러지스 인코포레이트 모션 시뮬레이터를 위한 리니어 액츄에이터
KR102588602B1 (ko) 2017-07-10 2023-10-11 디-박스 테크놀러지스 인코포레이트 모션 시뮬레이터를 위한 리니어 액츄에이터
WO2019026733A1 (fr) * 2017-08-03 2019-02-07 国際計測器株式会社 Procédé de test de pneu, dispositif de test de pneu et dispositif de dispersion
JP7444486B2 (ja) 2017-08-03 2024-03-06 国際計測器株式会社 タイヤ試験装置
CN108183578B (zh) * 2018-03-27 2024-04-02 河南凌翼智联装备有限公司 双子式同轴伺服驱动装置
CN108183578A (zh) * 2018-03-27 2018-06-19 河南凌翼智联装备有限公司 双子式同轴伺服驱动装置
CN108444730B (zh) * 2018-03-29 2024-04-09 中国汽车技术研究中心有限公司 一种商用车气压制动器扭转疲劳测试***
CN108444730A (zh) * 2018-03-29 2018-08-24 中国汽车技术研究中心有限公司 一种商用车气压制动器扭转疲劳测试***
ES2728422A1 (es) * 2018-04-23 2019-10-24 Jaroslav Rehak Motor eléctrico girando sobre el eje de rotación
CN109520733A (zh) * 2019-01-05 2019-03-26 中国船舶重工集团公司第七0三研究所 一种永磁联轴器的加载试验装置
CN109520733B (zh) * 2019-01-05 2023-12-05 中国船舶重工集团公司第七0三研究所 一种永磁联轴器的加载试验装置
CN109870360A (zh) * 2019-03-18 2019-06-11 吉林大学 一种曲轴可靠性试验装置
CN111076926A (zh) * 2019-12-12 2020-04-28 吉林大学 数控刀架三联齿盘可靠性试验台
JPWO2021225133A1 (fr) * 2020-05-08 2021-11-11
JP7338921B2 (ja) 2020-05-08 2023-09-05 国際計測器株式会社 車輪試験装置
WO2021225133A1 (fr) * 2020-05-08 2021-11-11 国際計測器株式会社 Dispositif d'essai de roue
CN113607408B (zh) * 2021-06-15 2024-02-27 金华卓远实业有限公司 一种中置电机齿轮测试机
CN113607408A (zh) * 2021-06-15 2021-11-05 金华卓远实业有限公司 一种中置电机齿轮测试机
CN113843691A (zh) * 2021-11-15 2021-12-28 周梅 一种机箱模具加工磨床
CN113843691B (zh) * 2021-11-15 2023-12-29 杭州丰衡机电有限公司 一种机箱模具加工磨床

Also Published As

Publication number Publication date
CN104737423A (zh) 2015-06-24
KR102079593B1 (ko) 2020-04-07
JP2019144249A (ja) 2019-08-29
JPWO2014058051A1 (ja) 2016-09-05
CN108663147A (zh) 2018-10-16
TWI623178B (zh) 2018-05-01
KR102190139B1 (ko) 2020-12-11
TW201818639A (zh) 2018-05-16
JP2018081103A (ja) 2018-05-24
KR20200036035A (ko) 2020-04-06
KR102190153B1 (ko) 2020-12-11
JP2022009438A (ja) 2022-01-14
TWI742658B (zh) 2021-10-11
JP2022009437A (ja) 2022-01-14
KR20200037412A (ko) 2020-04-08
KR102093861B1 (ko) 2020-04-14
JP2023054043A (ja) 2023-04-13
TW202032895A (zh) 2020-09-01
JP7389422B2 (ja) 2023-11-30
JP7001288B2 (ja) 2022-01-19
KR20180082629A (ko) 2018-07-18
JP6267289B2 (ja) 2018-01-24
TWI697179B (zh) 2020-06-21
JP6491732B2 (ja) 2019-03-27
JP2017022988A (ja) 2017-01-26
JP5986640B2 (ja) 2016-09-06
JP7240021B2 (ja) 2023-03-15
CN104737423B (zh) 2018-05-29
TW201424209A (zh) 2014-06-16
CN108616194B (zh) 2021-04-20
JP6746175B2 (ja) 2020-08-26
CN108663147B (zh) 2023-05-12
CN108616194A (zh) 2018-10-02
JP2020079811A (ja) 2020-05-28
KR20150070238A (ko) 2015-06-24

Similar Documents

Publication Publication Date Title
JP6491732B2 (ja) トルク付与ユニット及び駆動装置
CN109682564B (zh) 六自由度混联式电磁振动试验台
CN111220375A (zh) 具有柔性激励的多功能转子试验台
CN110036270A (zh) 用于电的机动车驱动器的能模块化构建的驱动系测试台
JP2013079823A (ja) ねじり試験機
CN106289771B (zh) 一种谐波齿轮减速器啮合扭转刚度的测量装置
JP5295348B2 (ja) 直動アクチュエータ及び機械試験機
CN110595763B (zh) 用于单输入双输出传动主轴***的振动试验装置
CN115096633B (zh) 一种滑台式电缸检测装置
CN212159014U (zh) 具有柔性激励的多功能转子试验台
JP2009276211A (ja) 継手装置および試験装置
WO2023195501A1 (fr) Dispositif de test, taille-haie et actionneur électrique
RU2349887C1 (ru) Вибростенд

Legal Events

Date Code Title Description
121 Ep: the epo has been informed by wipo that ep was designated in this application

Ref document number: 13845307

Country of ref document: EP

Kind code of ref document: A1

DPE1 Request for preliminary examination filed after expiration of 19th month from priority date (pct application filed from 20040101)
ENP Entry into the national phase

Ref document number: 2014540905

Country of ref document: JP

Kind code of ref document: A

NENP Non-entry into the national phase

Ref country code: DE

ENP Entry into the national phase

Ref document number: 20157012083

Country of ref document: KR

Kind code of ref document: A

122 Ep: pct application non-entry in european phase

Ref document number: 13845307

Country of ref document: EP

Kind code of ref document: A1