TW201333462A - Torsion testing device and mechanical testing device - Google Patents

Abstract

Provided is a torsion tester which comprises a sealed case accommodating a decelerator, and an oil cup. An internal space of the case and an internal space of the oil cup communicate with each other through a communication passage. A lubricant is filled into the case. When the lubricant in the case is thermally expanded, the surplus lubricant moves from within the case to the oil cup through the communication passage to be accumulated. When the volume of the lubricant in the case is decreased, the lubricant moves from the oil cup to within the case through the communication passage to fill the shortage so that the case always remains filled with the lubricant.

Description

Torsion tester and mechanical tester

The present invention relates to a mechanical testing machine for testing the mechanical properties of a test subject, and more particularly to a torsion testing machine for imparting a torsional load to a subject.

A servo motor type torsion tester that imparts a torsional load to a test object by the driving force of the servo motor has been put into practical use. As disclosed in Patent Document 1, the servo motor type torsion tester includes a speed reducer such as a planetary gear mechanism, and applies a large torsional load to the object to be measured.

The tooth surfaces of the gears constituting the gear mechanism of the reducer are provided with an oil film of lubricating oil such as grease to reduce the friction between the gears. For example, in a planetary gear type reducer, lubricating oil is retained at the bottom of the gearbox of the reducer, and only a part of the plurality of gears constituting the planetary gear mechanism is immersed in the lubricating oil. Then, the lubricating oil is sputtered by the gear mechanism to spread the lubricating oil throughout the gear mechanism. Further, the gear unit using the wave gear mechanism applies only the grease having a high viscosity to the tooth surface of the gear, and by rotating the gear mechanism, the oil film of the grease is uniformly formed on the tooth surface of each gear.

However, in the torsion test, in order to apply the reciprocating torsional load of the common region to the test object, the angle of the torsion test body is small, at most 10 degrees, and the amplitude of the reverse rotation is also less than 1 on the input shaft side of the reducer. Circle (360°). In such a use form, since only a very small portion of the tooth surface of the gear mechanism constituting the speed reducer is excessively used, an oil film is likely to be generated. In addition, the lubricating oil cannot be circulated throughout the gear mechanism, and sufficient heat dissipation effect cannot be obtained by the lubricating oil. In particular, when a servo motor having a high output of more than 10 kW is used, for example, when the servo motor is driven in reverse at a frequency of several tens of Hz, since a large amount of frictional heat is concentrated on the tooth surface of one of the gear meshes, sintering of the tooth surface is likely to occur.

Patent Document 2 describes a configuration in which a gear box of a reduction gear is filled with lubricating oil in order to reliably lubricate the meshing portion of the gear. However, since the gear box of the general reducer is sealed and the lubricating oil is filled in the gear box, the thermal expansion of the lubricating oil causes the pressure in the gear box to rise, which may cause the lubricating oil to escape from the oil seal and the like, and leak out to the gear box. In order to solve this problem, Patent Document 2 proposes a gear case having a mechanism for absorbing a change in internal pressure by changing the volume in the gear case.

[Previous Technical Literature] [Patent Literature]

[Patent Document 1] Japanese Patent Laid-Open Publication No. 2007-107955

[Patent Document 2] Japanese Patent Laid-Open No. Hei 7-310808

However, the internal pressure change absorbing mechanism of Patent Document 2 has a complicated structure, and since there is a movable portion, there is a problem that the manufacturing cost is high and the failure is easy.

An embodiment of the present invention provides a torsion testing machine including a servo motor and a speed reducer coupled to a servo motor, and repeatedly applying a torsional load to the object to be tested. The torsion testing machine comprises: a closed box, which houses a speed reducer; and an oil cup; the inner space of the box and the inner space of the oil cup are connected via a communication path, the box is filled with lubricating oil, and the lubricating oil in the box is thermally expanded, and the remaining When the lubricating oil is moved from the tank to the oil cup via the communication path and stored, and the lubricating oil in the tank is contracted or reduced, the insufficient lubricating oil is moved from the oil cup to the tank through the communication passage, and the inside of the tank is filled with lubricating oil at any time.

According to this configuration, since the entire gear constituting the speed reducer is always immersed in the lubricating oil, the tooth surface oil film can be prevented even if the reverse driving of less than one rotation is repeated. In addition, since it is cooled by a large amount of lubricating oil, even if the driving is reversed with a large torque and a high frequency, the frictional heat can be prevented from accumulating heat on the tooth surface, and sintering can be prevented. Further, even if the lubricating oil thermally expands, since the remaining portion moves to the oil cup, the pressure inside the reducer does not rise, for example, the lubricating oil does not leak from the oil seal to the outside of the tank, and pollutes around the torsion tester. Furthermore, even if the lubricating oil shrinks or decreases, It is possible to maintain the state of being filled with lubricating oil at any time in the tank, so that it is possible to surely prevent oil shortage or sintering. In addition, since the configuration is simple and there is no moving portion, the processing cost is low and the failure is unlikely to occur.

In addition, the oil cup may be disposed at a position higher than the box.

According to this configuration, as long as the lubricating oil enters the oil cup, the state in which the lubricating oil is filled in the tank of the speed reducer is maintained. In addition, it is easy to identify insufficient lubricant.

Further, the communication path may be formed by a pipe, and one end of the pipe is connected to the upper portion of the tank, and the other end is connected to the lower portion of the oil cup.

According to this configuration, when the lubricating oil of the reducer thermally expands, the gas remaining in the upper portion of the internal space of the reducer is discharged to the oil cup. In addition, since the lubricating oil is left at the lower end of the oil cup, when the temperature of the speed reducer is lowered and the lubricating oil in the box of the speed reducer is contracted, the lubricating oil is replenished from the oil cup to the box of the speed reducer.

Further, for example, a vent hole may be provided in the upper portion of the oil cup to maintain the internal space of the oil cup at atmospheric pressure.

According to this configuration, the pressure difference between the inside and the outside of the reducer can be eliminated, and the lubricating oil can be prevented from leaking out.

It is also possible to provide an air cleaner in the vent hole. Further, the output of the servo motor may be configured to be 10 kW or more.

According to an embodiment of the present invention, a subject having a first rotation axis and a second rotation axis that are not coaxial, includes: a first grip portion that holds the first rotation shaft; and a second grip portion that Holding the second rotating shaft; at least one of the first grip portion and the second grip portion is configured to be movable in a direction orthogonal to the rotation axis of at least one of the first grip portion and the second grip portion, and includes a driving means At least one of the first grip portion and the second grip portion is rotated about its rotation axis.

A power transmission device having an input/output shaft, such as a transmission, is generally not disposed coaxially with respect to an input shaft and an output shaft, and its arrangement differs depending on specifications. According to the above configuration, since the first grip portion that grips the first rotating shaft of the subject can be relatively moved in the direction orthogonal to the rotation axis, the second grip portion that grips the second rotating shaft can be relatively moved. The torsion test was performed on subjects of various specifications. Further, since the chuck is configured to move the chuck in two directions orthogonal to the rotation axis, the position of the chuck in the direction of the test axis does not fluctuate due to the movement of the chuck.

In addition, the first grip portion is configured to be non-rotating to the torsion tester body, and the second grip The holding portion is configured to rotate the torsion testing machine body, and the driving means may also constitute a rotational driving second grip portion.

Furthermore, the first grip can also be configured to move the torsion testing machine body in a direction orthogonal to the first axis of rotation.

According to this configuration, since the first grip portion has no rotation function, the structure is relatively simple and light in weight, the mechanism for moving the first grip portion does not require high load-bearing performance, and compact twist test can be realized. machine.

Further, the first grip portion may be configured to independently move in two orthogonal directions.

According to this configuration, the position of one of the two orthogonal directions is adjusted, and the other position is not changed, and the position adjustment of the first grip portion can be efficiently performed.

At least one of the first grip portion and the second grip portion may be configured to move in the direction of the rotation axis of the other grip.

A guide mechanism that guides one of the grip portions to move in the direction of the rotation axis of the grip portion may be provided.

According to this configuration, one of the grip portions can be correctly moved in the direction of the rotation axis of the grip.

The movable portion may be disposed on the substrate and provided with one grip portion, and a linear guide disposed between the substrate and the movable portion, and the movable portion is slidably supported by the movable portion. The direction of the rotation axis held by the holder.

According to this configuration, one of the grip portions can be accurately and smoothly moved in the direction of the rotation axis of the grip.

The movable portion may be configured to further include a locking mechanism that prevents the movable portion from moving in the direction of the rotation axis of the one grip portion.

According to this configuration, the grip portion is prevented from moving in the direction of the rotation axis during the test, and the test can be performed correctly.

The locking mechanism may also be configured to have a pressing pin that can be moved forward and backward to the linear guide, and the linear guide is pressed into the substrate side by the pressing pin, and the locking mechanism becomes the activity of the movable portion and is supported by the linear guide through the pressing pin. The state is such that the pressing pin is retracted, and when the front end of the pressing pin is separated from the linear guide rail, the linear guide rail is released to freely slide to support the movable portion, and the locking mechanism becomes a lock Set the state.

According to this configuration, the operation of the lock mechanism utilizes the weight of the movable portion, and the operation (locking)/release (unlocking) of the lock mechanism can be easily performed simply by advancing and retracting the squeeze pin toward the linear guide. Therefore, an effective locking mechanism can be realized simply.

The pressing pin may be configured to have a ball that is rotatably held at the front end portion, and has a male screw formed on the circumferential surface, and the locking means includes a pressing pin supporting member that is fixed to the movable portion and is formed to be coupled to the pressing pin. The female thread can switch between the locked state and the active state by rotating the pressing pin that is coupled to the pressing pin supporting member.

With this configuration, the locking mechanism can be operated simply by rotating the pressing pin. In addition, the friction force between the pressing pin and the linear guide rail is small, and the locking mechanism can be operated by rotating the pressing pin with a relatively weak force.

According to an embodiment of the present invention, a torsion testing machine for imparting a torsional load to a subject is provided. The torsion testing machine according to the embodiment of the present invention may be configured to include a driving unit that rotationally drives one end of the subject around a designated central axis, the driving unit includes a rotating portion, and the bearing portion is rotatably supported by the frame a rotating portion; and a motor that drives the rotating portion; the rotating portion includes: a torque sensor that detects a torsional load applied to the object to be tested; and a chuck that is disposed at one end of the rotating portion for one end of the subject And a shaft portion connecting the torsion sensor and the chuck; the bearing portion freely rotating to support the shaft portion. Further, a reaction force portion may be provided which fixes the other end of the subject.

According to this configuration, the torsion force applied to the input shaft of the subject can be controlled, and the torsion test can be performed. In addition, since the weight of the chuck is supported by the bearing portion, it is not applied to the torque sensor. Further, since the shaft portion disposed between the torsion sensor and the chuck is rotatably supported by the bearing portion, the torsion force applied to the chuck (that is, the torsional load imparted to the subject) is hardly passed through the shaft portion. Transmitted to the torque sensor. Therefore, the test load given to the test object can be correctly detected by the torque sensor.

The motor may also be a servo motor and include a speed reducer that decelerates the rotation of the output shaft of the servo motor and transmits it to the other end of the rotating portion. The speed reducer includes a bearing that rotatably supports the speed reducer. The output shaft, the torque sensor is connected to the output shaft of the reducer.

With this configuration, a servo motor type torsion tester which is easy to maintain can be realized. In addition, since the two ends support the torsion sensor in a beam shape and the torsion sensor can be freely rotated, only the torque imparted to the object to be tested is transmitted from the speed reducer to the torsion sensor without applying a large bending. Stress and shaft load, the torque sensor can more accurately detect the test load given to the test object.

The motor can also be used to reversely drive the rotating portion, and has a cable that is fixed at one end to the rotating portion, the other end is fixed to the fixed portion, and transmits a signal of the torque sensor; and a cable guiding portion that guides the accompanying rotating portion a cable that rotates and moves; the cable guiding portion includes a cylindrical outer peripheral surface that is coaxially disposed on the rotating portion, and a cable protection tube that is fixed at one end to the outer peripheral surface and the other end of which is substantially below the central axis of the rotating portion Fixed to the fixed portion, and accommodates the cable in the hollow portion; and the first guiding surface is curved, fixed to the frame, and formed substantially coaxially with the outer peripheral surface, and is substantially below the central axis from the central axis (0 degree) extends to an angular range of +90 degrees; the cable protection tube is configured to be freely bent around the axis parallel to the central axis, with a bending diameter above the minimum allowable bending diameter, and the outer peripheral surface is spaced from the first guiding surface, It is set to be roughly the same size as the outer diameter of the cable protection tube when the cable protection tube is bent with the specified minimum allowable bending diameter, and one part of the cable protection tube is elevated on the outer peripheral surface and the first Between guide surface, a portion of the overhead to a minimum allowable bending diameter of the bent schematic outline 180 degrees.

According to this configuration, since the cable protection tube for accommodating the cable does not have the degree of freedom of movement, the force generated by the free vibration of the cable and the cable protection tube is not imparted to the torque sensor, and the detection error of the torsional load can be reduced. In addition, noise can be prevented from occurring due to vibration of the cable protection tube; the cable protection tube collides with the frame or the test machine body; or the cable protection tube collides with each other to cause noise or damage to the device.

Further, the cable guiding portion may be configured to include a second guiding surface which is fixed to the frame and which is formed to be substantially coaxial with the outer peripheral surface, and is substantially directly below the central axis from the center axis (0 degree) When extending to an angle range of -90 degrees, the distance between the outer peripheral surface and the second guide surface is set to be approximately the same as the outer dimension of the outer peripheral surface in the radial direction when the cable protection tube is wound around the outer peripheral surface.

According to this configuration, since the cable protection tube is prevented from being shaken away from the lower surface of the outer peripheral surface, the detection error of the torsional load is reduced, and noise is prevented from being generated by the vibration of the cable protection tube; the cable protection tube collides with the frame or the test machine body; Because the cable protection tubes collide with each other Noise or damage to the unit.

Further, the third guide surface may be configured to have substantially the same curvature as the inner circumferential surface of the cable protection tube when the cable protection tube is bent at the minimum allowable bending diameter, and extend 180 degrees below the lower end of the second guide surface. .

Further, according to an embodiment of the present invention, a torsion testing machine for imparting a torsional load to a test object by a driving force of a motor is provided. A torsion testing machine according to an embodiment of the present invention includes: a first shaft that is rotatably supported by a bearing to the frame; and a torque sensor coupled to the motor via the first shaft to measure a torsional load; the second shaft The support is rotatably supported by the bearing to the frame; and the chuck is coupled to the torsion sensor via the second shaft for mounting at one end of the subject.

The mechanical testing machine according to an embodiment of the present invention may also be mechanically tested using a driving force of a servo motor. The servo motor includes a cylindrical motor case that houses a stator and a rotor, and a flange plate that is formed with a rotor. The extending rotating shaft penetrates the opening and is fixed to one end of the motor box; and the reaction force plate is fixed to the other end of the motor box; the flange plate and the reaction force plate are provided to be fixed to the frame of the mechanical testing machine. Screw holes are formed in the flange plate and the reaction force plate, respectively, and the flange plate and the reaction force plate are respectively fixed to the frame by screw holes. The mechanical testing machine is, for example, a torsion testing machine.

According to this configuration, since the motor case is supported at both ends, it is possible to suppress the precession movement of the rotary shaft which is generated only when the one end is unilaterally supported, and to stabilize the fixing of the motor case. This allows for highly accurate mechanical testing.

It is also possible to form a bearing for supporting the rotating shaft on the flange plate and the reaction force plate, respectively.

According to this configuration, since the rotating shaft is supported with higher rigidity, the rotating shaft is more stably held.

It is also possible to form a first (fourth) screw hole formed in the flange plate (reaction force plate) for fixing the servo motor and being parallel to the rotation axis of the servo motor.

According to this configuration, the servo motor can be supported with high rigidity particularly in the direction of the rotation axis.

It is also possible to form a second (third) screw hole in the flange plate (reaction force plate), and the second (third) screw hole is used to fix the axis of the servo motor parallel to the rotation axis of the servo motor. .

According to this configuration, the servo motor can be supported with high rigidity particularly in the direction orthogonal to the rotation axis.

The servo motor may further comprise a motor cover covering the motor case. The motor cover covers the flange plate and the reaction plate at both ends of the rotating shaft direction, and respectively engages with the respective sides, and the flange plate and the reaction A second screw hole for fixing the servo motor is formed on a side surface of at least one of the force plates, and a notch portion is formed at at least one end portion of the motor cover in the rotation axis direction to expose the second screw hole and its periphery.

A ventilation port may be formed in the motor cover, and further includes a ventilation fan attached to the ventilation port, and the notch portion extends to the inner side in the direction of the rotation axis of the flange plate or the reaction force plate, and the connection is formed. The internal space and external space between the motor box and the motor cover.

According to this configuration, the notch portion functions as a ventilating port for discharging heat in the servo motor to the outside (or introducing external cold air into the servo motor), thereby improving the air cooling performance of the servo motor. In particular, since the notch portion is formed in the vicinity of the flange plate and the reaction force plate which are easy to store heat, the flange plate and the reaction force plate can be effectively cooled.

An embodiment of the present invention provides a servo motor including a cylindrical motor case that houses a stator and a rotor, and a flange plate that is formed with an opening penetrating from a rotating shaft extending from the rotor and fixed to the motor case. One end; the flange plate is fixed to one end of the motor case by three or more pairs of bolts symmetrically arranged on the axis of rotation.

According to this configuration, for example, even if the servo motor is driven at a large output exceeding 10 kW, the motor case does not substantially move, and the motor case can be supported with high rigidity via the flange plate. Further, since a plurality of bolts arranged symmetrically with respect to the rotation axis are fixed, the motor case is supported with a substantially uniform rigidity irrespective of the rotation angle of the rotation shaft, and the sway of the rotation shaft can be suppressed.

It is also possible to arrange the plurality of bolts on concentric circles centered on the rotation axis.

According to this configuration, since the rotating shaft is supported by the bolts in a substantially uniform rigidity, the rotating shaft can be more uniformly supported with respect to the rotation angle.

The cross-sectional shape of the motor box can also be formed into a generally square shape, and the plurality of pairs of snails The plug contains two pairs of bolts symmetrically arranged on one of the diagonals of the square.

The flange plate may also be fixed to one end of the motor case by 8 bolts symmetrically arranged on the diagonal of the square.

According to this configuration, the fixing strength of the motor case to the flange plate is improved, and even when driven at a high output, the vibration accompanying the driving can be suppressed.

Further, the output of the servo motor may be 10 kW or more.

According to an embodiment of the present invention, sintering of the reducer can be prevented by a simple configuration without a movable portion.

100,200,300,400‧‧‧Twist test machine

110,210,310,410‧‧‧ seats

120,220,320,420‧‧‧Drive Department

130,230,330,430‧‧‧Responsive force department

121,131,221,231,321,331,421‧‧‧ chuck

122,222,322,422‧‧‧Servo motor

122a‧‧‧Motorbox

122b‧‧‧Motor cover

122b1‧‧‧Gap section

122b2‧‧‧ openings

122b3‧‧‧Motor cover

122c‧‧‧Flange plate

122d‧‧‧ Output shaft

122e‧‧‧Cooling fan

122e1‧‧‧Fan box

122e2‧‧‧ finger shield

122e3‧‧‧Flange

122e4‧‧‧Maintenance board

122e5‧‧‧Bend

122f‧‧‧Flange face

122h‧‧‧ openings

122r‧‧‧reaction board

123,223,324,424‧‧‧Reducer

123a, 223a‧‧ box

123b‧‧‧ input shaft

124‧‧‧Drive Department Framework

124a‧‧‧ horizontal board

124b‧‧‧ vertical board

124b1‧‧‧ openings

124c‧‧‧ reinforcing plate

124d‧‧‧Motor support frame

125,225‧‧‧Pipe

126,226‧‧‧ oil cup

126a‧‧‧Ventinel

126b‧‧‧Air filter

131‧‧‧ chuck

132‧‧‧Responsive force framework

132a‧‧‧ horizontal board

132b‧‧‧ vertical board

133,233,323,423‧‧‧torential sensor

134‧‧‧ Spindle

135‧‧‧ bearing

141‧‧‧ Input Department

141a‧‧‧ grip

142‧‧‧Output Department

142a‧‧‧ Main Department

142b‧‧‧Flange

142c‧‧‧ grip

223c‧‧‧Lubricant entrance

223d‧‧‧Lubricant export

227‧‧‧Drive Department Framework

227a‧‧‧ horizontal board

227b‧‧‧ vertical board

227c‧‧‧ reinforcing plate

228‧‧‧ Cover

228a‧‧‧air inlet

228b‧‧‧Exhaust port

251‧‧‧ pump

252‧‧‧cooler

253‧‧‧Pipe

260‧‧‧cooling plate

261‧‧‧ openings

262‧‧‧ Cooling water path

263‧‧‧ Cooling water introduction path

264‧‧‧Cooling water drainage path

332a‧‧‧first substrate

332b‧‧‧second substrate

332c‧‧ Track

332d‧‧‧ bearing

332e‧‧‧ditch

332f‧‧‧Flange

332g‧‧‧Flange

332n‧‧‧Corner Nut

332o‧‧‧Flange

332r‧‧‧ activity block

333‧‧‧ first activity board

333a‧‧‧through hole

333b‧‧‧feed screws

333c‧‧‧ nuts

333d‧‧‧ track

333e‧‧‧ bearing

333f‧‧‧Flange

333g‧‧‧ditch

334‧‧‧Second activity board

334a‧‧‧through hole

334b‧‧‧feed screws

334c‧‧‧ nuts

335a‧‧‧ pinion

335b‧‧‧Rotary axis

335c‧‧‧ worm gear

335d‧‧‧Rotary axis

336‧‧‧Floating mechanism

336a‧‧‧Axis

336a1‧‧‧ bottom plate

336a2‧‧‧Cylinder

336b‧‧‧ bearing department

336b1‧‧‧through hole

336c‧‧‧Squeeze pin

336d‧‧‧ ball

336e‧‧ balls

340‧‧‧ Cover

341,342,343‧‧‧Active cover unit

423a‧‧‧ spacers

425‧‧‧ cable bracket

425a‧‧‧End

425b‧‧‧The other end

426, 427‧‧‧ first and second cable bracket guides

426a, 426b, 427a‧‧ ‧ guide surface

428‧‧‧ Spindle

429‧‧‧ bearing

THD1, THD2, THS, THC1, THC2, THC3, THC4‧‧‧ female thread

B1, B2, B3, B4‧‧‧ bolts

H, H1, H2, H3‧‧‧ handles

H5, H6, H7, H8, H9, H10‧‧‧ holes

N1, N2, N3‧‧‧ nuts

W1, W2, W3, W4‧‧‧ gasket

S1‧‧1 first gap

S2‧‧‧ second gap

S3‧‧‧ third gap

S4‧‧‧4th gap

SH‧‧‧spline hole

The first drawing is a side view of a torsion testing machine according to a first embodiment of the present invention.

The second drawing is a side view of a servo motor according to a first embodiment of the present invention.

The third drawing is a rear view of the servo motor of the first embodiment of the present invention.

The fourth drawing is a front view of the servo motor of the first embodiment of the present invention.

The fifth figure is an enlarged view of part A of the second figure.

Fig. 6 is a side view showing the vicinity of a connecting portion between a servo motor and a speed reducing machine according to the first embodiment of the present invention.

Figure 7 is a side view of a coupling according to a first embodiment of the present invention.

Figure 8 is a rear elevational view of the input portion of the coupling of the first embodiment of the present invention.

Fig. 9 is a side view of the input portion of the coupling according to the first embodiment of the present invention as seen from the direction B in the eighth drawing.

Fig. 10 is a front elevational view showing the output portion of the coupling of the first embodiment of the present invention.

Figure 11 is a side view of the output portion of the coupling of the first embodiment of the present invention as seen from the direction C in the tenth diagram.

Figure 12 is a side view of a torsion testing machine of a second embodiment of the present invention.

Figure 13 is a front elevational view of a torsion testing machine in accordance with a second embodiment of the present invention.

Figure 14 is a view showing the first alternative example of the torsion testing machine of the second embodiment of the present invention. But the block diagram of the organization.

Fig. 15 is a side view showing a servo motor and a speed reducer of a configuration of a cooling mechanism of a second alternative example of the torsion testing machine according to the second embodiment of the present invention.

Fig. 16 is a perspective view showing a cooling plate of a second alternative example of the torsion testing machine according to the second embodiment of the present invention.

Figure 17 is a side view of a torsion testing machine according to a third embodiment of the present invention.

Fig. 18 is a front elevational view showing the reaction force portion of the torsion testing machine of the third embodiment of the present invention.

Fig. 19 is a side view showing a reaction force portion of a torsion testing machine according to a third embodiment of the present invention.

Fig. 20 is a cross-sectional view showing the vicinity of a floating mechanism (locking mechanism) of a reaction force portion of a torsion testing machine according to a third embodiment of the present invention.

A twenty-first drawing is a side view of a driving portion of a torsion testing machine according to a fourth embodiment of the present invention.

The twenty-second figure is an A-A arrow direction view of the twenty-first figure.

(First embodiment)

Hereinafter, embodiments of the present invention will be described in detail using the drawings. The first drawing is a side view of a torsion testing machine 100 according to a first embodiment of the present invention. The torsion testing machine 100 includes a driving unit 120 and a reaction force unit 130 that are attached to the base 110.

The drive unit 120 includes a servo motor 122, a speed reducer 123, and a chuck 121 for holding a subject. The chuck 121 is coupled to the output shaft of the servo motor 122 via a speed reducer 123. When the servo motor 122 is rotationally driven, the rotational motion of the output shaft is decelerated by the speed reducer 123, and then transmitted to the chuck 121 to rotate the chuck 121. Further, the main body of the servo motor 122 and the case 123a of the reducer 123 are fixed to the base 110 via the drive unit frame 124.

In the following description of the first embodiment, the direction of the rotation axis of the chuck 121 (the horizontal direction in the first drawing) is defined as the X-axis direction, and the vertical direction (the upper and lower directions in the first drawing) Set to the Z-axis direction and the horizontal direction orthogonal to both the X-axis and the Z-axis (No. The direction perpendicular to the paper surface in one figure is set to the Y-axis direction.

The reaction force portion 130 includes a reaction force portion frame 132, a torque sensor 133, a main shaft 134, a bearing 135, and a chuck 131 for gripping the subject. The torque sensor 133, the main shaft 134, and the chuck 131 are arranged in this order in the X-axis direction and integrally coupled. The reaction force portion frame 132 includes a horizontal plate 132a disposed on the base 110 and a vertical plate 132b integrally fixed to the horizontal plate 132a by welding. The vertical plate 132b has its normal line arranged in the X-axis direction.

The torsion sensor 133 is fixed to the vertical plate 132b of the reaction force portion frame 132 at one end in the X-axis direction (the left end of the first figure), and is coupled to the main shaft 134 at the other end (the right end of the first figure) in the X-axis direction. The main shaft 134 is disposed such that the central axis is oriented in the X-axis direction and is rotatably supported by the bearing 135 fixed to the horizontal plate 132a.

In this manner, the torque sensor 133, the main shaft 134, and the chuck 131 are coaxially coupled to form a shaft body extending in the X-axis direction, but the shaft body is fixed to the reaction force portion frame 132 only at one end thereof (the left end of the first figure). When the servo motor 122 is driven while the chuck 121 of the driving unit 120 and the chuck 131 of the reaction force unit 130 are gripping the subject, the subject is twisted. At this time, the torsional load applied to the subject is transmitted to the torque sensor 133 via the chuck 131 and the main shaft 134 with substantially no loss, and is measured by the torque sensor 133.

The reaction force portion frame 132 can move the base 110 in the X-axis direction by a moving mechanism (for example, a feed screw mechanism) provided on the base 110. The movement of the base 110 is performed by rotating the handle H disposed at one end of the base 110. In the present embodiment, the reaction force portion frame 132 is configured to move the driving portion 120 fixed to the base 110 in the X-axis direction by the moving mechanism. Therefore, the interval between the chuck 131 and the chuck 121 can be changed according to the length of the subject, and the torsion test can be performed on the subject of various lengths by one torsion testing machine 100. Further, when the torsion test is performed, the reaction force portion frame 132 and the base 110 are fastened by bolts (not shown), and the reaction force portion frame 132 is strongly fixed to the base 110.

Next, a configuration in which the main body of the servo motor 122 and the case 123a of the speed reducer 123 are supported by the drive unit frame 124 will be described.

The drive unit frame 124 is a structural member formed by integrally joining four steel sheets (a horizontal plate 124a, a vertical plate 124b, and a pair of reinforcing plates 124c) by welding. The lower end of the vertical plate 124b vertically disposed on the X-axis and the X-axis direction of the horizontal plate 124a disposed on the base 110 The ends (the left end of the first figure) are joined to form an L-shaped angle. Further, the horizontal plate 124a and the vertical plate 124b are also joined to a pair of reinforcing plates 124c arranged perpendicularly to the respective plates 124a and 124b to reinforce the L-shaped angle structure. Further, the drive unit frame 124 includes a motor support frame 124d that is fixed to the pair of reinforcing plates 124c. The reaction force plate 122r of the servo motor 122, which will be described later, is fixed to the motor support frame 124d, and the reaction force plate 122r is supported from below.

As shown in the first figure, the motor support frame 124d extends to the end opposite to the output shaft of the servo motor 122 (the right end of the first figure), and at its position, the reaction plate 122r of the servo motor 122 is bolted, and The reaction plate 122r is supported below.

Further, an opening 124b1 penetrating in the X-axis direction is provided in the vertical plate 124b. A box 123a of the speed reducer 123 is inserted into the opening 124b1, and a flange portion provided on the outer circumference of the box 123a is bolted to the vertical plate 124b. Thereby, the box 123a of the speed reducer 123 is integrally fixed to the drive unit frame 124 (that is, integrally with the base 110).

Further, the flange plate 122c of the servo motor 122 is fixed to the case 123a of the speed reducer 123, and is supported by the drive unit frame 124 via the case 123a of the speed reducer 123. In addition, the servo motor 122 is also supported by the drive unit frame 124 in the reaction force plate 122r. In the prior torsion tester, since the servo motor 122 is supported only by the flange plate 122c, when a strong fluctuation torque is applied to the output shaft 122d (second diagram) of the servo motor 122, the output shaft 122d is generated to be fixed to the flange plate 122c. Bearing (not shown) as a fulcrum precession motion (swing head movement). In particular, when the motor is driven by an output of more than 10 kW, the vibration of the precessional motion causes a noise that cannot be ignored in the measurement result, and there is a problem that the measurement accuracy is lowered. In the present embodiment, by adopting a configuration in which the servo motor 122 is supported by the reaction force plate 122r in addition to the flange plate 122c, the precessional movement of the output shaft 122d is suppressed, even when the servo motor 122 is driven at a high output. High precision testing is still possible. Further, since the bending stress applied to the rotating shafts of the servo motor 122 and the speed reducer 123 accompanying the precessing motion is also suppressed, the life of each device is also improved.

In the present embodiment, as described above, the servo motor 122 is supported on the flange surface 122f (second view) of the flange plate 122c and the reaction force plate 122r, and the servo motor 122 can be supported even at other positions.

Next, the structure of the servo motor 122 of this embodiment will be described. The second figure is a side view of the servo motor 122, and the third view is the servo motor 122 viewed from the side of the reaction force plate 122r. Rear view.

As shown in the second figure, the servo motor 122 has a motor case 122a, a motor cover 122b, a flange plate 122c, a reaction force plate 122r, an output shaft 122d, and two cooling fans 122e.

The motor case 122a is a substantially square cylindrical case formed by a thick metal plate, and houses a stator and a rotor (not shown) for driving the output shaft 122d. The flange plate 122c and the reaction force plate 122r are substantially square metal plates having the same thickness or more as the motor case 122a. The flange plate 122c and the reaction force plate 122r are attached to both ends of the motor case 122a in the cylinder axis direction (X-axis direction), and block the opening of the cylindrical motor case 122a. Bearings (not shown) that support the output shaft 122d are attached to the flange plate 122c and the reaction force plate 122r, respectively. An opening 122h (fourth view) is provided in the flange plate 122c, and one end of the output shaft 122d protrudes from the opening 122h outside the motor case 122a. Further, most of the side of the motor case 122a is covered by the motor cover 122b. The motor cover 122b is fixed to the flange plate 122c and the reaction force plate 122r so as to ensure a certain gap with the motor case 122a.

As described above, in the present embodiment, the reaction force plate 122r of the servo motor 122 is supported from below by the motor support frame 124d (first figure). As shown in the second and third figures, a pair of female threads THD1 are formed under the reaction force plate 122r. In the present embodiment, the servo motor 122 can be fixed to the motor support frame 124d by screwing the female thread THD1 through a through hole (not shown) provided in the motor support frame 124d.

Further, as shown in the third figure, a pair of female threads THS are respectively formed on both side faces (left and right sides of the third figure) of the reaction force plate 122r in the horizontal direction. Further, as shown in the second figure, a pair of female threads THD2 are also formed under the flange plate 122c.

The servo motor 122 of the present embodiment is designed by the torsion testing machine 100 (first drawing). For example, the servo motor 122 can be tilted by 90 degrees around the output shaft 122d, and the position of the female thread THS is fixed to the motor supporting frame. 124d (first picture). Or in order to further reduce the vibration of the servo motor 122 (for example, to increase the rigidity of the support structure of the servo motor, the resonance frequency is higher than the test frequency band), in addition to the female thread THD1, the bolt is also screwed into the female thread THS and THD2, while the servo motor 122 is strongly fixed by the motor support frame 124d.

The fourth view is a front view of the servo motor 122 viewed from the side of the flange plate 122c. The flange plate 122c is strongly fixed to the motor case 122a by four pairs of bolts B1. Each pair of bolts B1 Do not be placed in the four corners of the flange plate 122c of the outline square. Further, each pair of bolts B1 are arranged symmetrically with respect to a square diagonal line passing through the corner portions of the arrangement. Further, at each corner portion of the flange plate 122c, four through holes H1 for fixing the servo motor 122 are formed on a diagonal line passing through the corner portion thereof. Further, the four pairs of bolts B1 are symmetric with respect to the output shaft 122d and are disposed on concentric circles centered on the output shaft 122d. The four through holes H1 are also disposed on concentric circles centered on the output shaft 122d. As described above, by arranging the bolt B1 and the through hole H1 at the four corners of the flange plate 122c that is separated from the output shaft 122d, the flange plate 122c and the motor case 122a can be fixed with high strength in the bending direction of the output shaft 122d. Further, by arranging the bolt B1 and the through hole H1 to the output shaft 122d symmetrically and at equal angular intervals (90° intervals), the flange plate 122c and the motor are fixed with substantially the same strength with respect to the rotation angle of the output shaft 122d. Since the rotation angle causes the fluctuation of the support strength of the output shaft 122d to be small, the vibration of the output shaft 122d in the radial direction can be suppressed.

Two openings (not shown) are formed on the upper surface of the motor cover 122b, and a cooling fan 122e is attached to the opening. Cooling air is supplied to the gap between the motor case 122a and the motor cover 122b by the cooling fan 122e, and the motor casing 122a is cooled by the cooling air. As shown in the second and third figures, two notch portions 122b1 are formed on the lower side of the end portion of the reaction cover 122r side of the motor cover 122b. A pair of openings 122b2 that connect the internal space (the gap between the motor case 122a and the motor cover 122b) and the external space are formed by the two notch portions 122b1. The cooling air warmed by the heat of the motor case 122a is discharged to the outside from the opening 122b2.

As described above, the servo motor 122 of the present embodiment can provide the opening 122b2 away from the reaction force plate 122r (especially the female screw THD1) by providing the notch portion 122b1. Therefore, even if the flange plate 122c is fixed to the motor support frame 124d, the opening 122b2 can be blocked by the motor support frame 124d without hindering the cooling of the motor case 122a by the cooling fan 122e, which can be in the motor cover 122b and the motor case 122a. A large flow of cooling air is supplied to achieve a high cooling effect.

Further, the cooling fan 122e is attached to the motor cover 122b by fixing the fan case 122e1 to the motor cover 122b by tightening the bolt B2. Further, a lattice-like finger cover 122e2 for preventing a finger or the like from contacting the blade of the cooling fan 122e is attached to the upper surface of the fan case 122e1. The finger guard 122e2 is also mounted by a bolt B2. The fifth figure is an enlarged view of the vicinity of the bolt B2 (the enlarged view of the portion A of the second figure).

The finger guard 122e2 is disposed on the flange portion 122e3 extending in the horizontal direction from the upper edge of the frame-shaped fan case 122e1. A holding plate 122e4 is interposed between the flange portion 122e3 and the finger cover 122e2.

The finger guard 122e2 is formed by bending a steel wire, and a part thereof is a bent portion 122e5 bent in a U shape, and a bolt B2 for fixing the finger cover 122e2 can pass therethrough. Further, holes H2 and H3 for passing the bolts B2 are formed in the holding plate 122e4 and the flange portion 122e3. The bolt B2 passes through the curved portion 122e5, the holes H2 and H3, and is fastened by attaching the nut N1 to the bolt B2, so that the curved portion 122e5, the retaining plate 122e4, and the flange portion 122e3 are at the head B2a of the bolt B2 and the snail. The state of fastening between the caps N1. Further, spacers W1 and W2 are provided between the head portion B2a of the bolt B2 and the curved portion 122e5, and between the flange portion 122e3 and the nut N1. Since the fastening force of the bolt B2 can be surely transmitted to the curved portion 122e5, the holding plate 122e4, and the flange portion 122e3 via the spacers W1 and W2, the finger cover 122e2 is strongly fixed to the fan case 122e1 by a high fastening force. .

Further, as shown in the fifth figure, the screw portion B2b of the bolt B2 penetrates the nut N1 and passes through the hole H4 formed in the upper surface 122b3 of the motor cover 122b. The upper surface 122b3 of the motor cover 122b is formed in a state in which the inner and outer surfaces thereof are screwed into the nuts N2 and N3 of the bolt B2 and fastened. In addition, the fastening force of the bolt B2 can be surely transmitted to the motor cover 122b, and the gasket W3 is sandwiched between the nut N2 and the motor cover upper surface 122b3, between the motor cover upper surface 122b3 and the nut N3. The spacer W4 is sandwiched.

According to the above configuration, the servo motor 122 of the present embodiment is strongly fixed to each other by the finger guard 122e2, the holding plate 122e4, the fan case 122e1, and the motor cover 122b via the bolt B2, so that the servo motor 122 is driven by the finger cover when the servo motor 122 is driven. The vibration suppression of 122e2 is minimal. In particular, the gaskets W1, W2, W3, and W4 are fastened to prevent vibration.

Next, a connection structure between the servo motor 122 of the torsion testing machine 100 and the speed reducer 123 of the present embodiment will be described. The sixth drawing is a side view of the vicinity of the connection portion between the output shaft 122d of the servo motor 122 and the input shaft 123b of the speed reducer 123 in the present embodiment.

As shown in the sixth embodiment, in the present embodiment, the output shaft 122d of the servo motor 122 and the input shaft 123b of the speed reducer 123 are coupled by a coupling 140. The coupling 140 is extremely rigid (for example, rigidly connected to the output shaft 122d of the servo motor 122 or more). The shaft, the rotational motion of the output shaft 122d of the servo motor 122 is highly reactive to the input shaft 123b of the reducer 123. Since the torsion testing machine 100 of the present embodiment is mainly used for a fatigue tester that applies a torsional load to and from a subject, if the rigidity of the coupling is low, the servo motor is reversely driven at a high frequency (with a short round trip period). When the output shaft 122d of 122 is rotated, the rotational vibration is absorbed by the coupling and is not correctly transmitted to the input shaft 123b of the speed reducer 123. In the present embodiment, by using the high-rigidity coupling 140, it is possible to impart a very high frequency fluctuation load to the subject. In other words, when the torsion testing machine 100 of the present embodiment is used, the number of times of repetition per unit time of the repetitive load applied to the subject can be increased, and the time required for the fatigue test can be greatly shortened. In addition, since higher-frequency rotational vibration can be imparted to the subject, tests with higher energy and more stringent conditions can be performed.

Next, the configuration of the coupling 140 will be described. As shown in the sixth diagram, the coupling 140 has an input portion 141 that connects the output shaft 122d of the servo motor 122, and an output portion 142 that connects the input shaft 123b of the speed reducer 123. The input unit 141 and the output unit 142 are integrally coupled by two pairs of bolts B3 and B4. The bolt B3 is inserted from the input portion 141 side, and the bolt B4 is inserted from the output portion 142 side.

A side view of the coupling 140 is shown in the seventh diagram. In addition, the bolts B3 and B4 are omitted in the seventh drawing. As shown in the seventh figure, the input unit 141 is a member having a substantially cylindrical shape. Further, the output portion 142 is an auxiliary cylindrical member having a substantially cylindrical main portion 142a and a flange portion 142b formed at one end of the main portion 142a (the right end of the seventh drawing). A hole H5 through which the output shaft 122d (sixth figure) of the servo motor 122 passes is formed in the input portion 141. Further, a spline hole SH through which the input shaft 123b (sixth figure) of the speed reducer 123 passes is formed in the output portion 142.

The flange portion 142b of the output portion 142 is formed to have substantially the same diameter as the input portion 141, and when coupled to the input portion 141, a pair of female screws (described later) that screw the bolt B3 and a hole H6 that passes through the bolt B4 are formed. Similarly, a pair of holes (described later) that pass through the bolt B3 and a female screw THC1 that is screwed into the bolt B4 are formed in the input portion 141.

The eighth diagram is a rear view of the input portion 141 viewed from the side of the servo motor 122. Further, the ninth diagram is a side view of the input portion 141 viewed in the direction indicated by the arrow B in the eighth diagram. As shown in the eighth drawing, a pair of holes H7 passing through the bolt B3 and a female screw THC1 screwing into the bolt B4 are formed in the input portion 141, respectively. Further, a hole H7 and a female thread THC1 are formed at the center of the input portion 141. The cylindrical surface centered on the shaft (one point chain line in the eighth figure).

As shown in the ninth diagram, the input portion 141 is formed with a first slit S1 that is cut in a plane perpendicular to the central axis of the input portion 141. As shown in the eighth figure, the front end of the first slit S1 reaches the maximum diameter portion (i.e., the diameter portion) of the input portion 141. Further, in the input portion 141, a portion (the grip portion 141a) on the back side (the servo motor 122 side) of the first slit S1 is formed with a second slit S2 that is cut in a plane including the central axis of the input portion 141.

As shown in the eighth and ninth diagrams, the hole H8 and the female thread THC2 that face each other across the second slit S2 are formed in the grip portion 141a of the input portion 141. The hole H8 is formed coaxially with the female screw THC2, and by inserting a bolt into the hole H8 and screwing it into the female thread THC2, the grip portion 141a is fastened to the direction in which the width of the second slit S2 is reduced, and the diameter of the hole H5 is reduced. The inner diameter of the hole H5 is slightly larger than the outer diameter (the sixth drawing) of the output shaft 122d of the servo motor 122 in a state where the grip portion 141a is not fastened, and is fastened by being attached to the hole H8 and the female thread THC2. In the holding portion 141a, the output shaft 122d is fastened to the inner peripheral surface of the hole H5 having a reduced diameter, and the output shaft 122d is strongly gripped by the grip portion 141a.

In the present embodiment, as described above, the first slit S1 is formed in the input unit 141, and the second slit S2 for gripping the output shaft 122d is formed only in the grip portion 141a on the back side of the first slit S1. Therefore, even if the grip portion 141a is fastened by the bolt, only the vicinity of the second slit S2 of the grip portion 141a is deformed, and the other portion (for example, the rigid portion 141c on the side of the output portion 142 from the first slit S1) is not deformed. The shaft can be connected with high precision.

The first slit S1 is not provided, and the second slit S2 extends to the front surface of the input unit 141 (the left side surface of the ninth diagram) (that is, the rigid body portion 141c is not provided, and the entire input portion 141 is configured as the grip portion 141a). In order to sufficiently reduce the second slit S2, the force required to deform the input portion 141 is excessively large. In the present embodiment, the input portion 141 is divided into the grip portion 141a and the other portion by the first slit S1. When the output shaft 122d is fastened, the load applied to the input portion 141 can be suppressed to the minimum necessary. size.

Next, the configuration of the output unit 142 will be described. The tenth view is a front view of the output portion 142 viewed from the side of the speed reducer 123. Further, the eleventh diagram is a side view of the output portion 142 viewed in the direction indicated by the arrow C in the tenth diagram. As shown in the tenth diagram, a pair of holes H6 through which the bolts B4 pass and a female thread THC3 into which the bolts B3 are screwed are formed in the flange portions 142b of the output portion 142. In addition, The hole H6 and the female thread THC3 are formed on a cylindrical surface (a dot chain line of a tenth figure) centering on the central axis of the output portion 142.

As shown in the eleventh diagram, a third slit S3 that is cut into a plane perpendicular to the central axis of the output portion 142 is formed in the main portion 142a of the output portion 142. As shown in the tenth diagram, the front end of the third slit S3 reaches the diameter portion of the main portion 142a of the output portion 142. In the main portion 142a, a portion (the grip portion 142c) on the front side (the side of the speed reducer 123) of the third slit S3 is formed with a fourth slit S4 that is cut in a plane including the central axis of the output portion 142.

As shown in the tenth and eleventh diagrams, in the grip portion 142c of the output portion 142, two pairs of holes H9 and female threads THC4 that face each other across the fourth slit S4 are formed. Each of the pair of holes H9 and the female screw THC4 are formed coaxially, and by inserting a bolt into the hole H9 and screwing it into the female thread THC4, the grip portion 142c is fastened in the direction in which the width of the fourth slit S4 is reduced, and the spline hole SH is contracted. A spline having a shape corresponding to the spline hole SH is formed at a distal end portion of the input shaft 123b (sixth drawing) of the speed reducer 123, and is inserted into the hole H9 by inserting the front end of the input shaft 123b into the spline hole SH. When the grip portion 142c is fastened with the bolt of the female thread THC4, the inner circumferential surface of the spline hole SH is in close contact with the outer circumference of the input shaft 123b, and the input shaft 123b is strongly gripped by the grip portion 142c.

As shown in the sixth embodiment, in the present embodiment, in order to reduce the inertia of the speed reducer 123 and the coupling 140, the diameter of the input shaft 123b of the speed reducer 123 is formed to be narrower than the output shaft 122d of the servo motor 122. Therefore, it is not easy for the output portion 142 to hold the shaft sufficiently firmly with the surface pressure as the input portion 141. Therefore, in the present embodiment, the connecting portion between the input shaft 123b of the speed reducer 123 and the coupling 140 is of a spline structure, and the input shaft 123b of the speed reducer 123 can be firmly held even if the small surface pressure does not slide. .

In the present embodiment, as described above, the third slit S3 is formed in the output portion 142, and the fourth slit S4 for gripping the input shaft 123b is formed only on the front side of the third slit S3. Therefore, even if the grip portion 142c is fastened by the bolt, only the vicinity of the fourth slit S4 of the grip portion 142c is deformed, and the other portion (for example, the flange portion 142b on the input portion 141 side than the third slit S3) It can be connected to the shaft with high precision without deformation.

The third slit S3 is not provided, and the fourth slit S4 extends to the previous configuration of the back surface of the output portion 142 (the upper surface of the eleventh diagram) (that is, the entire output portion 142 including the flange portion 142b is configured as the grip portion 142c) In order to sufficiently narrow the fourth slit S4, the output portion 142 is changed. The force required for the shape is excessive. In the present embodiment, the output portion 142 is divided into the grip portion 142c and other portions by the third slit S3. When the input shaft 123b is fastened, the load applied to the output portion 142 can be suppressed to the minimum necessary. size.

Next, the lubrication method of the speed reducer 123 will be described. The speed reducer 123 of the present embodiment is a speed reducer using a planetary gear mechanism, and a plurality of gears constituting the planetary gear mechanism are fixed or axially supported inside the case 123a (sixth figure). In the present embodiment, in order to reduce the frictional force between the plurality of gears constituting the planetary gear mechanism, heat generation due to the frictional force and wear of the gear are prevented, and the lubricating oil is filled in the inside of the tank 123a which is oil-tightly formed without a gap. In the previously constructed reducer, only one part of the gear mechanism is immersed in the lubricating oil remaining in the bottom of the gear case, and the gear is rotated to carry the lubricating oil and spread over the entire gear mechanism. However, in the present embodiment, since the speed reducer 123 is mainly used for the torsion testing machine 100 for performing the fatigue test, the input shaft 123b can be repeatedly reversed with a rotation angle of less than one rotation (for example, the rotation angle is amplitude 30° rotation vibration). Such a method of use does not allow the lubricating oil to spread over the entire gear mechanism for the previously constructed reducer, and an oil film is generated between the gears, which may cause excessive heat generation and wear of the gear. In addition, especially when the output motor is reversely driven by a high output motor of 10 kW or more, the heat generated by the friction between the gears is increased. If the gears are not always immersed in the lubricating oil, heat is accumulated in the gears and sintering may occur. .

In the present embodiment, since the lubricating oil is filled in the inside of the tank 123a without a gap as described above, even when the fatigue test is performed by the torsion testing machine 100, the oil film is not generated between the gears. Further, even if the driving is reversed by a high output motor at a frequency (for example, 20 Hz), sintering does not occur.

Further, in the present embodiment, as shown in the sixth embodiment, a hole H10 which is in contact with the inside of the tank 123a is formed in the upper portion of the tank 123a. A pipe 125 extending above is attached to the hole H10, and an oil cup 126 (first figure) is attached to the front end of the pipe 125. Further, the oil cup 126 is disposed at a position higher than the tank 123a.

When the torsion testing machine 100 is operated, the temperature inside the tank 123a of the speed reducer 123 rises due to the frictional heat of the gears in the speed reducer 123, and the lubricating oil filled in the inside of the tank 123a thermally expands. The configuration of the previous reducer in which the hole H10 is not formed in the case 123a of the reducer 123 is because the inside of the reducer 123 is a closed space, so that when the lubricating oil thermally expands, the lubricating oil becomes a high pressure. The oil may leak from a gap (for example, an oil seal portion) between the components constituting the tank 123a. In the present embodiment, since the lubricating oil which is thermally expanded flows to the oil cup 126 via the pipe 125, the lubricating oil does not leak. Further, when the torsion testing machine 100 is stopped and the inside of the tank 123a of the speed reducer 123 is cooled by natural heat radiation, the lubricating oil inside the tank 123a contracts, and the inside of the tank 123a becomes a negative pressure. Thus, the lubricating oil flowing to the oil cup 126 is returned to the tank 123a. Further, even if the lubricating oil in the tank 123a is reduced due to aging of the lubricating oil or the like, the reduced portion is replenished from the oil cup 126, and the inside of the tank 123a is always kept filled with the lubricating oil. Further, a vent hole 126a is provided in the upper portion of the oil cup 126, and the inner space of the oil cup 126 is always at atmospheric pressure. Further, the air cleaner 126b is provided in the vent hole 126a of the oil cup 126, and since the outside air enters the oil cup 126 via the air cleaner 126b, impurities are prevented from being mixed into the lubricating oil.

The above is the description of the first embodiment of the present invention. As described above, the torsion testing machine 100 of the present embodiment is characterized by the support structure of the servo motor 122, the structure of the coupling 140 that connects the servo motor 122 and the reduction gear 123, and the gear lubrication method inside the reduction gear 123.

(second embodiment)

Next, a second embodiment of the present invention will be described. The torsion testing machine 200 according to the second embodiment of the present invention described below has a feature of a cooling mechanism including a reduction gear in addition to the features of the first embodiment. Fig. 12 is a side view showing the torsion testing machine 200 of the second embodiment of the present invention.

Similarly to the torsion testing machine 100 of the first embodiment, the torsion testing machine 200 of the present embodiment includes a base 210 and a driving unit 220 and a reaction force unit 230 disposed on the base 210, and are respectively provided for driving. The subject 220 and the chucks 221 and 231 of the reaction force unit 230 are attached to the subject, and the servo motor 222 of the drive unit 220 is driven to apply a torsional load to the subject. The chuck 221 on the driving unit 220 side and the servo motor 222 are connected via the speed reducer 223; the servo motor 222 and the speed reducer 223 are connected by a rigid coupling; and the lubricating oil is filled in the box 223a of the speed reducer 223 The oil cup 226 is connected to the portion of the tank 223a via the pipe 225, and the like, and is also the same as the first embodiment.

Further, similarly to the first embodiment, in the following description of the second embodiment, the rotation axis direction of the chuck 221 (the left-right direction of the twelfth diagram) is defined as the X-axis direction. The vertical direction (the upper and lower directions in the twelfth figure) is defined as the Z-axis direction, and the direction orthogonal to both the X-axis and the Z-axis (the direction perpendicular to the paper surface of the twelfth image) is set to the Y-axis direction.

The thirteenth view is a front view of the torsion testing machine 200 viewed from the side of the servo motor 222. The drive unit 220 includes a drive unit frame 227 that is movable in the X-axis direction on the housing 210. The servo motor 222 main body and the box 223a of the speed reducer 223 are fixed to the drive unit frame 227, and are integrally formed with the drive unit frame 227 so as to be movable in the X-axis direction. The torsion testing machine 200 of the present embodiment can adjust the interval between the chucks 221 and 231 by the movement of the driving unit frame 227, and can perform the torsion test on the subject of various lengths. The drive unit frame 227 includes a horizontal plate 227a, a vertical plate 227b, and a pair of reinforcing plates 227c disposed on the base 210.

The horizontal plate 227a is horizontally disposed on the base 210. Further, the vertical plate 227b is disposed perpendicular to the X-axis, and is integrally fixed by welding the lower end and one end portion (the left end of the first figure) on the upper surface of the horizontal plate 227a in the X-axis direction to form an L-shaped angle. An opening penetrating through the X-axis direction is provided in the vertical plate 227b, and a box 223a of the speed reducer 223 is inserted into the opening, and the flange portion of the outer periphery of the box 223a of the speed reducer 223 is fixed to the vertical plate by bolts. At 227b, the box 223a of the speed reducer 223 is fixed integrally with the drive unit frame 227 (i.e., integrally with the base 210).

As shown in Fig. 12, the reinforcing plate 227c is disposed at a corner formed by the horizontal plate 227a and the vertical plate 227b, and is welded to both the horizontal plate 227a and the vertical plate 227b. The vertical plate 227b is reinforced by the reinforcing plate 227c, and the vertical plate 227b is strongly fixed to the horizontal plate 227a.

As shown in the thirteenth diagram, the pair of reinforcing plates 227c are disposed such that the servo motor 222 and the speed reducer 223 are interposed from both sides in the Y-axis direction. A cover 228 covering the reducer 223 is provided between the pair of reinforcing plates 227c.

The outer cover 228 has an air inlet 228a and an exhaust port 228b that connect the inside and the outside of the outer cover 228. As shown in Fig. 12, the intake port 228a is provided below the servo motor 222 on the side of the outer cover 228 (the left side of the twelfth figure). Further, a through hole 227d through which an air duct (not shown) connected to the exhaust port 228b passes is formed in each of the reinforcing plates 227c, and the exhaust port 228b is formed at a position facing the through hole 227d.

In the present embodiment, the air blower or the fixed point cooler is connected to the air duct, and the cooling air is blown into the outer casing 228 to cool the speed reducer 223 disposed inside the outer casing 228. The exhaust port 228b functions as an exhaust port of the cooling air blown into the inside of the outer cover 228 via the intake port 228a. Features.

As described above, in the present embodiment, the cooling of the speed reducer 223 is performed by air cooling. However, the cooling of the speed reducer 223 can also be performed by other means. The configuration of the cooling mechanism of the first and second alternative embodiments of the present embodiment in which other cooling mechanisms are assembled will be described with reference to Figs. 14 to 16 .

A block diagram showing the configuration of the cooling mechanism of the first alternative example is shown in Fig. 14. The cooling mechanism of the first other example performs the cooling of the speed reducer 223 by circulating cooling lubricating oil for lubricating the gear of the speed reducer 223. That is, the lubricating oil inlet 223c and the lubricating oil outlet 223d which are in contact with the inside of the tank 223a are formed in the tank 223a of the speed reducer 223, and the lubricating oil inlet 223c, the lubricating oil outlet 223d, and the lubricating oil circulation are connected via the piping 253. The pump 251 and the cooling machine 252 for lubricating the lubricating oil circulate the lubricating oil in the order of the pump 251 → the inside of the tank 223a → the cooler 252 → the pump 251. The gears inside the reducer 223 are cooled by continuously supplying the lubricating oil cooled by the cooler 252 to the inside of the tank 223a of the speed reducer 223.

Further, in the first alternative example, as described above, since the gear is lubricated by the lubricating oil, the oil cup serving as the lubricating oil reservoir is not provided. Further, for example, a storage tank for storing lubricating oil may be provided between the tank 223a of the speed reducer 223 and the cooler 252.

Next, a cooling mechanism according to a second alternative example of the second embodiment will be described. The fifteenth diagram is a side view showing the servo motor 222 and the speed reducer 223 which constitute the cooling mechanism of the second alternative example. As shown in Fig. 15, in the second alternative example, a cooling plate 260 is provided between the servo motor 222 and the box 223a of the speed reducer 223.

Fig. 16 shows a perspective view of the cooling plate 260. The cooling plate 260 is a plate-shaped member formed of a material having high thermal conductivity (metal or the like). As shown in Fig. 16, an opening 261 through which the connecting portion between the speed reducer 223 and the servo motor 222 passes is formed in the center of the cooling plate 260. Further, a cooling water path 262 is formed inside the cooling plate 260 so as to surround the opening 261. Further, inside the cooling plate 260, a cooling water introduction path 263 and a cooling water drainage path 264 that connect the cooling water path 262 and the cooling plate 260 are provided.

In the second example, the cooling water path 262 is connected to the pump and the cooling water cooling device via the cooling water introduction path 263 and the cooling water drainage path 264, and the cooling water is guided by the pump → cooling water introduction path 263 → the cooling water path 262. →Cooling water drainage path 264→Cooling water cooling Device → pump cycle. The heat generated by the speed reducer 223 is absorbed by the cooling water cooled by the cooling water cooling device via the cooling plate 260, and is discharged to the outside. As a result, the reducer 223 is cooled.

The above is a description of the second embodiment of the present invention.

The servo motor type torsion testing machine disclosed in Patent Document 1 (hereinafter referred to as "torsion testing machine") has a cylindrical motor case that houses a stator and a rotor, and is mounted in the axial direction of the motor case. Flange plate and reaction plate at both ends. A bearing that supports the output shaft of the servo motor is mounted on the flange plate and the reaction force plate. As a torsion testing machine of Patent Document 1, in a general servo motor used in a mechanical testing machine, a through hole for an output shaft is formed on a flange plate, and a servo motor is mounted on the testing machine by a bolt. A motor mounting hole (screw hole) on the frame, and the servo motor is fixed to the frame of the mechanical testing machine only in a beam-like manner at one end of the flange plate. Further, for example, four flange plate mounting holes for mounting the flange plate to the motor case are formed in the flange plate, and are attached to the motor case by four bolts.

In the previous servo motor type precision mechanical testing machine, a lower output servo motor of less than 10 kW was used, and as the servo motor type testing machine became popular, a servo motor type testing machine with higher output was required. In addition, high-output servo motors of more than 10 kW that can be used for high-frequency inversion driving, such as fatigue testing, have also been commercialized.

However, in the case of using a high-output servo motor of more than 10 kW, as in the torsion tester of Patent Document 1, when the servo motor is fixed to the frame of the test machine only by the flange plate, the support strength of the output shaft of the servo motor is insufficient to fix Centered on the bearing of the flange plate, the output shaft causes a precession motion (swing head motion), and the vibration generated by the precession motion causes a decrease in test accuracy.

In addition, in the case of using a high-output servo motor of more than 10 kW, as in the previous servo motor, the flange plate is fixed to the motor case with only four bolts, and the fixing strength of the motor box is insufficient, and precession motion or the like is not required. The vibration of the motion causes the test accuracy to decrease.

According to the configuration of the first and second embodiments of the present invention described above, it is possible to suppress the swinging motion (precession motion, etc.) of the output shaft which occurs when the servo motor is driven in reverse with high output, and the test accuracy is improved.

Further, Patent Document 1 discloses a torsion testing machine including a rotation side holding body (driving portion) that rotatably holds one end of a subject, and a fixed side holder that keeps the other end of the subject from rotating. (reaction force portion), the subject to be tested via the rotating side holder A torsion force imparting means for imparting a torsion force and a torsion force detector for detecting a torsion force imparted to the subject. The torque detector is provided on the fixed side holding body. When such a torsion tester is used to perform a torsion test of a power transmission device such as a propeller shaft, the input shaft of the power transmission device is held by the rotation side holding body, and the output shaft is held by the fixed side holder, and the input is performed. The shaft imparts torque. The torque of the output shaft is then detected by a torque detector.

The power transmission device imparts a varying torque generated by the motor in use to the input shaft. Therefore, the output shaft of the power transmission device is held by the reaction force portion, and the input shaft is held by the drive portion, and the torsional test of the torsional load applied to the input shaft is performed to evaluate the fatigue performance of the power transmission device.

As described in the above Patent Document 1, the prior torsion testing machine has the rotating side holding body and the fixed side holding body disposed coaxially. However, in a power transmission device having a gear mechanism such as a shifting device, the input shaft and the output shaft are generally not disposed coaxially, and the positional relationship varies depending on the specifications. Therefore, the previous torsion tester in which the rotation side holding body and the fixed side holder are disposed coaxially is not able to perform the fatigue test (torsion test) of the power transmission device having the gear mechanism such as the transmission.

According to the configuration of the third embodiment of the present invention described below, it is possible to perform a torsion test of a subject having two rotation axes that are not coaxially arranged.

(The third embodiment)

Next, a third embodiment of the present invention will be described. Figure 17 is a side view of a torsion testing machine 300 according to a third embodiment of the present invention. The torsion testing machine 300 of the present embodiment is a testing device suitable for torsion testing of an object having an input shaft and an output shaft that are not disposed coaxially, such as an automobile shifting unit. For example, the torsion tester 300 can be used to perform a durability test (fatigue test) of applying a torsional torsional load to the subject.

The torsion testing machine 300 is configured such that a driving portion 320, a reaction force portion 330, and a cover 340 are disposed on the base 310. Chasing plates 321 and 331 are respectively provided in the driving unit 320 and the reaction force unit 330 (eighteenth drawing). The torsion test is performed in a state where the input shaft and the output shaft of the subject are fixed to the chucks 321 and 331, respectively.

In the following description of the third embodiment, the axial direction of the torsion test (the left-right direction of the seventeenth diagram) is defined as the X-axis direction, and the horizontal direction orthogonal to the X-axis (vertical) The direction of the paper surface in the seventeenth image is set to the Y-axis direction, and the vertical direction (the upper and lower directions in the seventeenth image) is set to the Z-axis direction.

When the cover 340 is subjected to the torsion test, the lubricating oil of the test object or the fragment of the damaged subject is scattered to the outside of the device, and the opening and closing cover covering the main portion of the torsion testing machine 300 from the driving portion 320 to the reaction force portion 330 is covered. . As shown in Fig. 17, the cover 340 is constituted by three movable cover units 341 to 343 which are different in size and can be moved in the X-axis direction. The movable cover units 341, 342, and 343 are formed such that the sizes of the Y-axis and the Z-axis are gradually increased in this order, and when the subject is attached to (or folded down) the torsion testing machine 300, the movable cover unit 343 is used. Moving in the positive X-axis direction (the right direction of the seventeenth image), the movable cover units 341 and 342 are housed in the movable cover unit 343 in a nested manner.

The chuck 321 is connected to an output shaft (not shown) of the servo motor 322 via a torque sensor 323 and a speed reducer 324. The rotational motion of the output shaft of the servo motor 322 is decelerated by the speed reducer 324 and transmitted to the chuck 321, so that the chuck 321 rotates around the axis parallel to the X-axis. Further, the chuck 331 (eighteenth drawing) of the reaction force portion 330 is locked without moving when the torsion test is performed. Therefore, in a state where the input shaft and the output shaft of the subject are fixed to the driving unit 320 and the reaction force unit 330, the servo motor 322 is driven to apply a torsional load to the subject. The torsional load applied to the subject is measured by the torque sensor 323.

The torsion testing machine 300 of the present embodiment performs a torsion test for a gear unit of various specifications in which the relativeities of the input and output shafts are arranged differently, and the position of the chuck 331 can be adjusted in the X-axis, Y-axis, and Z-axis directions. In order to perform such adjustment, the torsion testing machine 300 includes a chuck moving mechanism that moves the position of the chuck 331 in the Y-axis and the Z-axis direction, and a position in which the reaction force portion 330 provided with the chuck 331 is moved to the X-axis. The reaction force moving mechanism of the direction.

Next, the chuck moving mechanism will be described. The eighteenth view is a front view of the reaction force portion 330 viewed from the side of the driving portion 320 (i.e., the negative X-axis direction). Further, the nineteenth view is a side view of the reaction force portion 330 viewed in the negative direction of the Y-axis. As shown in FIGS. 17 to 19, the reaction force portion 330 includes a first substrate 332a disposed on the base 310 of the torsion testing machine 300, and is disposed perpendicular to the X-axis and fixed to the first substrate 332a. The second substrate 332b.

A pair of rails 332c extending in the Y-axis direction are attached to both end portions of the second substrate 332b facing the driving portion 320 in the Z-axis direction. The first flap 333 is coupled to the pair of rails 332c It is sandwiched and slidably held along the rail 332c in the Y-axis direction. Further, as shown in FIG. 19, at the end portion of each of the rails 332c in the positive X-axis direction (the end away from the second substrate 332b), a flange portion which protrudes in a direction (Z-axis direction) opposite to the pair of rails 332c is provided. 332f, the cross section of each of the rails 332c is formed in an L shape. Further, at one of the Z-axis directions of the first movable plate 333, a pair of flange portions 333f protruding in the Z-axis direction along the second substrate 332b are formed. The flange portion 333f of the first movable plate 333 is inserted into the concave portion formed by the second substrate 332b and each of the rails 332c without any gap. Thereby, the first movable panel 333 is held by the flange portion 332f of each of the rails 332c so as not to be separated from the state sandwiched by the pair of rails 332c.

Further, a plurality of grooves 332e extending in the Y-axis direction are formed on the second substrate 332b. The groove 332e has a wide groove width at the bottom and has a substantially T-shaped cross-sectional shape. A rectangular flange portion 332g is formed in the groove 332e, and a corner nut 332n having a substantially T-shaped longitudinal section is inserted. The corner nut 332n is held in the groove 332e so as to be freely movable only in the Y-axis direction. Further, the diagonal length of the flange portion 332o of the corner nut 332n is longer than the width of the groove 332e of the accommodation flange portion 332o, and the corner nut 332n cannot rotate in the groove 332e. Further, a plurality of through holes 333a (eighteenth drawing) are provided at a position of the first movable plate 333 opposite to the groove 332e. When the torsion test is performed, the bolt B5 passing through the through hole 333a is screwed into the corner nut 332n, and the first movable plate 333 and the second base plate 332b are fastened between the bolt B5 and the corner nut 332n to move the first movable plate. 333 is strongly fixed to the second substrate 332b, and the first movable plate 333 is locked so as not to move in the Y-axis direction. Further, by fastening the bolt B5 and the corner nut 332n, the first movable plate 333 can be moved in the Y-axis direction while the bolt B5 is attached to the corner nut 332n.

The first movable plate 333 is driven in the Y-axis direction by a feed screw structure composed of a feed screw 333b and a nut 333c. The feed screw 333b has its axis oriented in the Y-axis direction, and is rotatably supported by a pair of bearings 332d provided at the upper end of the second substrate 332b. Further, the nut 333c is fixed to the first movable plate 333. Therefore, when the feed screw 333b is rotated, the first movable plate 333 moves together with the nut 333c in the axial direction (Y-axis direction) of the feed screw 333b.

The handle H1 can be attached to one end of the feed screw 333b, and when the first movable plate 333 is moved in the Y-axis direction, the handle H1 is attached to the feed screw 333b, and the feed screw 333b is rotated by manually operating the handle H1.

Two in the Y-axis direction of the face of the first movable plate 333 opposite to the driving portion 320 The end is mounted with a pair of rails 333d extending in the Z-axis direction. The second movable plate 334 is sandwiched by the pair of rails 333d, and is slidably held along the rail 333d in the Z-axis direction. The rail 333d and the second flap 334 have the same coupling structure as the rail 332c and the first flap 333, and are held so that the second flap 334 is not detached from the state sandwiched by the pair of rails 333d.

Further, a pair of grooves 333g along the Z-axis direction are formed in the first movable plate 333. Similarly to the groove 332e, the groove 333g has a substantially T-shaped longitudinal section, and a corner nut (not shown) having a substantially T-shaped longitudinal section is inserted into the groove 333g. Further, a plurality of through holes 334a are also provided at a position of the second movable plate 334 opposite to the groove 333g. When the torsion test is performed, the second movable plate 334 and the first movable plate 333 are fastened between the bolt B6 and the corner nut by screwing the bolt B6 passing through the through hole 334a into the corner nut, and the second movable plate is pressed. The first movable plate 333 is strongly fixed to the first movable plate 333, and the second movable plate 334 is locked so as not to move in the Z-axis direction. Further, by fastening the bolt B6 and the corner nut, the second movable plate 334 can be moved in the Z-axis direction while the bolt B6 is attached to the corner nut.

The second movable plate 334 is driven in the Z-axis direction by a feed screw mechanism composed of a feed screw 334b and a nut 334c. The feed screw 334b has its axis oriented in the Z-axis direction and is rotatably supported by a pair of bearings 333e provided on the first movable plate 333. Further, the nut 334c is fixed to the second movable plate 334. Therefore, when the feed screw 334b is rotated, the second movable plate 334 moves together with the nut 334c in the axial direction (Z-axis direction) of the feed screw 334b.

The handle H2 can be attached to one end of the feed screw 334b, and when the second movable plate 334 is moved in the Z-axis direction, the handle H2 is attached to the feed screw 334b, and the feed screw 334b is rotated by the operation handle H2.

Thus, by operating the handle H1, the first movable plate 333 can move the first and second substrates 332a, 332b of the reaction force portion 330 in the Y-axis direction, and further, by operating the handle H2, the second movable plate can be made. 334 pairs of the first movable plate 333 are moved in the Z-axis direction. As shown in the eighteenth diagram, the chuck 331 of the reaction force portion 330 is provided on the second movable plate 334. Therefore, the position of the chuck 331 can be adjusted in the Y-axis direction and the Z-axis direction by operating the handles H1 and H2.

Next, the reaction force portion moving mechanism will be described. As shown in the eighteenth and nineteenth views, a pair of tracks 311 along the X-axis direction are fixed on the base 310. Further, as shown in Fig. 19, on each of the rails 311, the two movable blocks 332r are slidably coupled along the rails 311. These movable blocks 332r are mounted below the first substrate 332a. That is, the reaction force portion 330 is movable along the rail 311 in the X-axis direction.

Further, as shown in Fig. 19, a rack 312 along the X-axis direction is fixed to the upper surface of the base 310. Further, a pinion 335a that is coupled to the rack 312 is provided in the vicinity of the lower surface of the first substrate 332a. The pinion gear 335a is coaxially fixed to a lower end of the rotating shaft 335b extending through the first substrate 332a and extending in the Z-axis direction. Further, the rotating shaft 335b is rotatably supported by the first substrate 332a. Therefore, when the rotating shaft 335b is rotated, the pinion 335a also rotates, and the pinion 335a receives the reaction force from the coupled rack 312. Then, the reaction force portion 330 is driven by the reaction force received by the pinion 335a, and the movable block 332r is guided to the engaged track 311 to move in the X-axis direction.

A worm wheel 335c is coaxially fixed to the upper end of the rotating shaft 335b. The worm wheel 335c is coupled to a worm formed on a rotating shaft 335d extending in the Y-axis direction. Further, a handle H3 can be attached to the rotating shaft 335d. Therefore, when the handle H3 attached to the rotating shaft 335d is rotated, the rotating shaft 335d rotates around the axis parallel to the Y-axis. Then, the worm wheel 335c is driven by the rotation of the worm shaft of the rotating shaft 335d coupled thereto, and the worm wheel 335c integrally rotates around the axis parallel to the Z axis with the rotating shaft 335b and the pinion 335a, and the pinion 335a is detached from the rack. 312 receives the reaction force in the X-axis direction, and the reaction force portion 330 moves along the rail 311. Therefore, by operating the handle H3, the position of the reaction force portion 330 in the X-axis direction can be adjusted.

In addition, the handles H1, H2 and H3 are detachable and can be removed during the torsion test to avoid the impact test.

Further, only when the position of the reaction force portion 330 is adjusted, the reaction force portion 330 can be smoothly moved in the X-axis direction to the base 310, and the reaction force portion is fixed to the base 310 in order to secure the reaction force portion 330 during the test. 330 has a floating mechanism 336. The floating mechanism 336 is disposed between the first substrate 332a and the movable block 332r. When the reaction force portion 330 is moved in the X-axis direction, the floating mechanism 336 causes the lower surface of the reaction force portion 330 (the lower surface of the first substrate 332a) to float from the base 310, and only supports the reaction force portion with the movable block 332r and the rail 311. The total load of 330 (i.e., the linear sliding mechanism constituted by the movable block 332r and the track 311 is effective). In addition, when the torsion test is performed, the floating mechanism 336 does not apply the entire load (or most of) of the reaction force portion 330 to the movable block 332r and the track 311, and the first substrate 332a is directly placed on the base 310. (That is, the linear sliding mechanism is invalidated).

The twentieth figure is a cross-sectional view of the periphery of the floating mechanism 336 of the reaction force portion 330. As shown in the twentieth diagram, the floating mechanism 336 includes a shaft portion 336a, a bearing portion 336b, and a pressing pin 336c. The shaft portion 336a has a member that is fixed to the bottom plate portion 336a1 on the upper surface of the movable block 332r and a cylindrical portion 336a2 that extends from the center of the upper surface of the bottom plate portion 336a1 in the Z-axis direction. The bearing portion 336b is a member fixed to the first substrate 332a of the reaction force portion 330, and has a cylindrical hollow portion that slidably accommodates the cylindrical portion 336a2 of the shaft portion 336a in the Z-axis direction. Further, the bearing portion 336b supports the outer peripheral surface of the cylindrical portion 336a2 via the ball 336e which is the rotator, and can move the shaft portion 336a in the Z-axis direction with extremely low frictional resistance.

As shown in the twentieth diagram, a through hole 336b1 extending in the Z-axis direction and having the same diameter as the pressing pin 336c is provided on the upper surface of the bearing portion 336b. Further, a female thread is formed in the through hole 336b1. The pressing pin 336c is formed with a male screw that is coupled to the through hole 336b1 on the side surface. Further, a metal ball 336d rotatably supported by the body of the pressing pin 336c is disposed at the lower end of the pressing pin 336c, and a portion of the ball 336d protrudes from the lower end of the body of the pressing pin 336c. The pressing pin 336c is screwed into the through hole 336b1 so that the ball 336d faces the upper surface of the shaft portion 336a.

When the reaction force portion 330 is moved, after the first substrate 332a is loosened to the bolt B7 of the base 310, the pressing pin 336c is rotated in the downward direction, and the ball 336d is abutted against the shaft portion 336a. Above. Further, when the pressing pin 336c is rotated, the shaft portion 336a and the movable block 332r move downward to the first substrate 332a, and the lower surface of the reaction force portion 330 floats from the base 310, and the reaction force portion 330 becomes only by the movable block 332r and The state in which the track 311 is supported. Therefore, the reaction force portion 330 can be smoothly moved in the X-axis direction.

Further, when the torsion test is performed, the pressing pin 336c is rotated in the upward direction, and the first substrate 332a is lowered. When the ball 336d is separated from the upper surface of the shaft portion 336a, the load on the movable block 332r and the rail 311 is not applied to the reaction force portion 330, and the first substrate 332a is placed directly on the base 310. Next, the first substrate 332a is fixed to the base 310 by a bolt B7. As shown in the twentieth diagram, the ball 336d is separated from the upper surface of the shaft portion 336a. In a state where the first substrate 332a is directly mounted on the base 310, the lower ends of the first substrate 332a and the bearing portion 336b are not coupled to the shaft portion 336a. contact. Therefore, in this state, the load of the reaction force portion 330 is not transmitted to the movable block 332r and the rail 311 at all, and a large load is applied to the reaction force portion 330. In the rotation test, the active block 332r is not excessively applied, and the movable block 332r is broken.

Further, by providing the ball 336d which can be rotated with low friction at the lower end of the pressing pin 336c, when the pressing pin 336c is screwed in toward the shaft portion 336a, or when the pressing pin 336c is separated from the shaft portion 336a, it is remarkably lowered. The amount of friction acting between the lower end of the pressing pin 336c and the upper surface of the shaft portion 336a allows the pressing pin 336c to rotate with a low torsion and suppresses the wear of the upper surface of the shaft portion 336a and the underside of the pressing pin 336c.

(Fourth embodiment)

Next, a fourth embodiment of the present invention will be described. In the prior torsion tester, a torsion sensor for detecting a torsional load was fixed in the reaction force plate, and the torque sensor connected to the signal cable itself did not rotate. That is, the previous torsion tester detects the torsion of the output shaft of the subject to be applied to the chuck fixed to the reaction disk side as a torsional load. However, when testing a power transmission component such as a shifting unit of a car, it is required to manage the load applied to the input shaft of the subject (that is, the load corresponding to the engine output). In particular, in order to more accurately evaluate the performance of a part having a speed ratio between the input/output shafts such as a shifting unit, it is necessary to arrange the torque sensor on the side of the driving portion to detect the torque applied to the input shaft of the subject. However, when the torsion sensor is disposed on the side of the driving portion, the torsion sensor is rotated together with the input shaft of the subject. Therefore, in the torsion test, the signal cable of the torsion sensor must be prevented from vibrating greatly to interfere with the torsion testing machine itself. The torsion testing machine 400 according to the fourth embodiment of the present invention described below is provided with a signal for preventing the torsion sensor. The cable interferes with the mechanism of the torsion tester.

The twenty-first drawing is a side view of the vicinity of the driving portion 420 of the torsion testing machine 400 according to the fourth embodiment of the present invention. In addition, since the structure of the movable part is the same as that of the third embodiment, detailed description is omitted.

As shown in the twenty-first embodiment, the drive unit 420 of the present embodiment is provided with a speed reducer 424 and a torque sensor 423 between the servo motor 422 and the chuck 421, similarly to the drive unit 320 of the third embodiment. And constitute. Further, the torque sensor 423 is fixed to the output shaft of the speed reducer 424 via a substantially cylindrical spacer 423a. In the present embodiment, as described above, the torque sensor 423 is provided on the side of the driving unit 420, and the size in the X-axis direction from the speed reducer 424 to the chuck 421 is large. Therefore, in the present embodiment, the main shaft 428 connecting the torsion sensor 423 and the chuck 421 can be rotatably supported by the bearing 429. In addition, the output shaft of the reducer 424 (no picture The bearing (not shown) provided in the box of the speed reducer 424 is also rotatably supported. That is, in the present embodiment, as shown in the twenty-first embodiment, the output shaft of the speed reducer 424 that is coupled to each other, the spacer 423a, the torque sensor 423, the main shaft 428, and the chuck 421 are attached to the main shaft 428 and The two output shafts of the reducer 424 are freely rotatable and supported with high rigidity.

Further, in the present embodiment, as described above, since the driving portion 420 is increased in size, the weight of the main shaft 428 is as light as possible to reduce the inertia of the rotating portion of the driving portion 420 (torque sensor 423, main shaft 428, and chuck 421). . Further, in order to minimize the frictional resistance in the bearing 429, the bearing 429 having a small frictional resistance is used, and the bearing 429 is mounted with a preload torque in a range where the frictional resistance does not increase. According to this configuration, even if the torque sensor 423 is disposed in the driving unit 420, the torsional load can be measured with high accuracy.

Next, a mechanism for preventing interference of the signal cable of the torque sensor 423 will be described. Figure 22 shows a cross-sectional view of the A-A of the twenty-first figure. In the present embodiment, the signal cable of the torque sensor 423 is housed in a cable holder 425 (Cable Bear).

The cable holder 425 is a flexible cable protection tube formed by connecting a plurality of frames into a row by a chain structure, and the signal cable passes through the inside. In addition, the frames of the cable holder 425 are connected to each other so as to be bendable only around a specific one axis (X axis in the present embodiment), and the cable holder 425 is only in a specific YZ plane (that is, the axis of the torsion test) It can be bent in one plane). In addition, the cable bracket 425 cannot be bent at a diameter smaller than the minimum allowable bending diameter.

One end 425a of the cable holder 425 is fixed to the outer peripheral surface of the spacer 423a. In addition, the other end 425b of the cable holder 425 is fixed to the base 410 of the torsion testing machine 400 at a position directly below the spacer 423a.

Further, first and second cable holder guides 426, 427 are fixed to the base 410. Each of the first and second cable holder guides 426, 427 has a cylindrical surface guide surface 426a, 427a that is substantially concentric with the spacer 423a. The guiding surface 426a of the first cable holder guide 426 is disposed adjacent to the spacer 423a from the vicinity of the lower end of the spacer 423a in the twenty-second diagram to the vicinity of the right end. Further, the interval between the outer peripheral surface of the spacer 423a and the guide surface 426a is set to be slightly larger than the thickness of the cable holder 425 (the radial dimension of the spacer 423a), and the cable holder 425 is not surrounded by the outer surface and the guide surface of the spacer 423a. 426a is sandwiched, and the cable holder 425 is in the spacer 423a The outer peripheral surface and the guide surface 426a are not vibrated, and the cable holder 425 can smoothly move in the gap between the outer peripheral surface of the spacer 423a and the guide surface 426a in accordance with the rotation of the spacer 423a. Further, the first cable holder guide 426 is formed with a guide surface 426b extending in the counterclockwise direction from the lower end of the guide surface 426a to the other end 425b of the cable holder 425 with a minimum allowable bending diameter (inner diameter) of the cable holder 425. Further, the guide surface 427a of the second cable holder guide 427 is disposed to face the spacer 423a from the vicinity of the lower end of the spacer 423a in the twenty-second diagram to the vicinity of the left end. The interval between the outer peripheral surface of the spacer 423a and the guide surface 427a is set to be slightly larger than the minimum allowable bending diameter (outer diameter) of the cable holder 425, and therefore, the guide surface 427a is formed to be smaller than the guide surface 426a of the first cable holder guide 426. The radius of curvature is large.

As shown by the two-dot chain line of the twenty-second figure, in the maximum counterclockwise vibration state of the spacer 423a, one end 425a of the cable holder 425 is located on the lower right side of the spacer 423a. At this time, the cable holder 425 extends clockwise from the one end 425a clockwise along the outer peripheral surface of the spacer 423a and the guiding surface 426a of the first cable holder guide 426, and then guides to the guiding surface 426b, and then extends counterclockwise to the other end 425b. .

When the spacer 423a rotates clockwise from this state, the other end 425b side of the cable holder 425 is slowly sent out from the guiding surface 426a of the first cable holder guide 426, away from the guiding surface 426b, and moved to the second cable holder guide 427. On the guiding surface 427a. Then, in the state where the spacer 423a is maximally clockwise, the cable holder 425 is shown by a broken line in the figure, and one end 425a is located on the lower left side of the spacer 423a. At this time, the cable holder 425 extends from the one end 425a clockwise along the outer peripheral surface of the spacer 423a, and then exits from the spacer 423a, and extends in the air in a counterclockwise direction with the minimum allowable bending of the cable holder 425. The guiding surface 427a of the cable holder guide 427 extends counterclockwise to the other end 425b.

In this embodiment, the signal cable of the torsion sensor 423 is controlled by the cable holder 425 so as not to jump out from the specific YZ plane, and the cable holder 425 is guided by the first and second cable holder guides 426 and 427, so the torque is applied. The signal cable of sensor 423 does not interfere with other portions of torsion testing machine 400. Further, by setting the interval between the outer peripheral surface of the spacer 423a and the guide surface 427a of the second cable holder guide 427 to be substantially the same as the minimum allowable bending diameter (outer diameter) of the cable holder 425, the outer circumference of the spacer 423a is Between the guiding faces 427a of the second cable bracket guide 427, the cable bracket 425 is folded back 180 degrees, and the cable bracket is further prevented. The 425 is bent at a diameter smaller than the minimum allowable bending diameter, and the cable holder 425 is prevented from being freely moved, causing the cable holder 425 to vibrate to collide with the spacer 423a or the guiding surface 427a. Further, even if the spacer 423a is rotated, the cable holder 425 is not bent below the minimum allowable bending diameter, causing the cable holder 425 or the signal cable to be broken.

In the case of evaluating the fatigue characteristics of the power transmission device, it is necessary to apply a torque corresponding to the output characteristics of the power unit such as an engine to the input shaft for testing. However, the previous torsion tester described in Patent Document 1 cannot detect and control the input. Torque of the shaft. For example, in the case of a power transmission device in which the input shaft and the output shaft of the transmission shaft rotate at the same number of revolutions (that is, the reduction ratio is 1), since the torque of the input shaft and the output shaft are the same, the torque detector detects The torque of the output shaft can accurately evaluate the fatigue characteristics. However, when the subject is a power transmission device having a reduction ratio such as a shifting device, since the torque applied to the input shaft and the output shaft is different, and the mechanical loss is also a size that cannot be ignored, the previous torsion tester cannot be very correct. The fatigue characteristics were evaluated.

According to the configuration of the fourth embodiment of the present invention described above, the torsion test capable of measuring the torsion applied to the input shaft of the subject can be performed.

The above is a description of an exemplary embodiment of the present invention. The embodiment of the present invention is not limited to the above description, and can be arbitrarily changed within the scope of the technical idea expressed by the description of the patent application.

For example, the above embodiment relates to a torsion tester, but the floating mechanism (locking mechanism) 336 can also be applied to various devices other than the torsion tester. For example, in the same manner as the torsion tester, there is a pair of chucks that sandwich the object to be tested, and various test machines (such as a tensile/compression tester or a vibration tester) that can adjust the chuck interval according to the size of the test object are also required. The above floating mechanism is applied. In addition, various mechanical testing machines, other testing, inspection, and observation devices (such as physical observation devices such as chemical analysis devices or astronomical telescopes), transport devices (such as large stage devices), and manufacturing devices can be constructed by moving all or part of the device. The above-described floating mechanism can also be applied to a processing device or the like.

100‧‧‧Twist test machine

124c‧‧‧ reinforcing plate

110‧‧‧ machine base

124d‧‧‧Motor support frame

120‧‧‧ Drive Department

125‧‧‧Pipe

130‧‧‧Responsive Forces Department

126‧‧‧ oil cup

121,131‧‧‧ chuck

126a‧‧‧Ventinel

122‧‧‧Servo motor

126b‧‧‧Air filter

122c‧‧‧Flange plate

132‧‧‧Responsive force framework

122r‧‧‧reaction board

132a‧‧‧ horizontal board

123‧‧‧Reducer

132b‧‧‧ vertical board

123a‧‧‧ box

133‧‧‧Torque sensor

124‧‧‧Drive Department Framework

134‧‧‧ Spindle

124a‧‧‧ horizontal board

135‧‧‧ bearing

124b‧‧‧ vertical board

H‧‧‧handle

124b1‧‧‧ openings

Claims (40)

A torsion testing machine includes a servo motor and a speed reducer coupled to the servo motor, and applies a torsional load to the object to be tested, and includes a sealed box that houses the speed reducer and an oil cup; and the inside of the box a space is communicated with the internal space of the oil cup via a communication passage, and the inside of the tank is filled with lubricating oil, and when the lubricating oil in the tank is thermally expanded, the remaining lubricating oil is moved from the tank to the oil cup via the communication passage and stored. When the lubricating oil in the tank is contracted or reduced, the insufficient lubricating oil is moved from the oil cup to the inside of the tank via the communication passage, and the inside of the tank is filled with lubricating oil at any time. The torsion testing machine of claim 1, wherein the oil cup is disposed at a position higher than the box. The torsion testing machine according to claim 1 or 2, wherein at least a part of the communication path is formed by a pipe, one end of the pipe is connected to an upper end of the tank, and the other end is connected to the oil cup. Lower end. The torsion testing machine of claim 2, wherein the inner space of the oil cup is maintained at atmospheric pressure. The torsion testing machine of claim 4, wherein a vent hole is provided in an upper portion of the oil cup. A torsion testing machine according to claim 5, wherein an air cleaner is provided in the aforementioned vent hole. The torsion testing machine according to any one of claims 1 to 6, wherein the output of the servo motor is 10 kW or more. a torsion testing machine for performing a torsion test on a subject having a first rotating shaft and a second rotating shaft that are not coaxially disposed, and comprising: a first grip portion that holds the first rotating shaft; a second grip portion that holds the second rotating shaft; and a driving means that rotationally drives the first grip portion and the second grip At least one of the ministries. At least one of the first grip portion and the second grip portion is configured to move in the direction orthogonal to the rotation axis of the at least one grip. The torsion testing machine of claim 8, wherein the first grip portion is configured to be non-rotatable to the torsion testing machine body, and the second grip portion is configured to rotate the torsion testing machine body, the driving means The aforementioned second grip portion is rotationally driven. The torsion testing machine according to claim 8 or 9, wherein the first grip portion is movable in a direction orthogonal to the first rotation axis of the torsion testing machine body. The torsion testing machine according to claim 10, wherein the first grip portion is configured to be independently movable in two orthogonal directions. The torsion testing machine according to any one of claims 8 to 11, wherein at least one of the first grip portion and the second grip portion is configured to be the other party Move in the direction of the rotation axis of the grip. The torsion testing machine according to claim 12, wherein the movable portion further includes a locking mechanism that prevents the one grip portion from moving in a direction of a rotation axis of the grip portion. The torsion testing machine according to claim 12, further comprising a guiding mechanism that guides the one grip portion to move in a direction of a rotation axis of the grip portion. The torsion testing machine according to claim 14, wherein the guiding mechanism includes: a substrate; a movable portion disposed on the substrate and having the one grip portion; and a linear guide disposed on the Between the substrate and the movable portion, the movable portion is supported so as to be slidable in a direction of a rotation axis of the one grip portion. For example, the torsion testing machine described in claim 15 of the patent application, wherein the aforementioned activity department The locking mechanism is provided in one step to prevent the movable portion from moving in the direction of the rotation axis of the one grip portion. The torsion testing machine according to claim 16, wherein the locking mechanism is configured to include a pressing pin that can be moved forward and backward toward the linear guide, and the linear guide is pressed into the substrate side by the pressing pin. The locking mechanism is configured such that the weight of the movable portion is supported by the linear guide via the pressing pin, and the pressing pin is retracted. When the front end of the pressing pin is separated from the linear guide, the linear guide is released. The movable portion is slidably supported, and the lock mechanism is in a locked state. The torsion testing machine according to claim 17, wherein the pressing pin has a ball that is rotatably held at the front end portion, and a male thread is formed on the circumferential surface, and the locking means is provided with a pressing pin supporting member. The locking mechanism is fixed to the movable portion, and a female screw that is coupled to the pressing pin is formed. The locking means is configured to switch between a locked state and an active state by rotating the pressing pin that is coupled to the pressing pin supporting member. A torsion tester is provided with a torsional load on a test object, and includes a drive unit that rotationally drives one end of the test subject around a designated central axis, the drive unit including a rotating portion and a bearing portion a frame that rotatably supports the rotating portion; and a motor that drives the rotating portion; the rotating portion includes: a torque sensor that detects a torsional load applied to the object to be tested; and a chuck that is coupled to the rotating portion One end of the portion is mounted to one end of the object to be tested; and a shaft portion that connects the torsion sensor and the chuck; the bearing portion rotatably supports the shaft portion. The torsion testing machine described in claim 19, wherein the aforementioned motor is used The motor is provided with a speed reducer that decelerates the rotation of the output shaft of the servo motor and transmits the rotation to the other end of the rotating portion. The speed reducer includes a bearing that rotatably supports the frame. An output shaft, the torque sensor is coupled to an output shaft of the reducer. The torsion testing machine according to claim 19, wherein the motor is for inverting and driving the rotating portion, and includes: a cable fixed at one end to the rotating portion and the other end fixed to the foregoing a fixing portion that transmits a signal of the torque sensor; and a cable guiding portion that guides the cable that moves in accordance with rotation of the rotating portion; the cable guiding portion includes a cylindrical outer peripheral surface that is coaxially disposed In the rotating portion, the cable protection tube is fixed to the outer peripheral surface at one end, and the other end is fixed to the fixing portion directly under the central axis of the rotating portion, and the cable is accommodated in the hollow portion; and the first guiding surface is The curved surface is fixed to the frame, and is formed substantially coaxially with the outer peripheral surface, and extends from the center of the central axis directly below (0 degrees) to an angle range of +90 degrees; the cable The protective tube system is configured to bend freely around a shaft parallel to the central axis, and has a bending diameter equal to or greater than a minimum allowable bending diameter, the outer peripheral surface and the first guiding The interval between the faces is set to be substantially the same as the outer diameter of the cable protection tube when the cable protection tube is bent by the specified minimum allowable bending diameter, and one of the cable protection tubes is elevated over the outer peripheral surface and the first guiding surface Between the one of the above-mentioned elevated portions, the roughened portion is roughly 180 degrees in a rough outline of the minimum allowable bending diameter. The torsion testing machine according to claim 21, wherein the cable guiding portion has a second guiding surface which is curved, fixed to the frame, and has an outer peripheral surface It is formed coaxially and coaxially, and extends from the center of the central axis (0 degrees) to an angle of -90 degrees around the central axis, and the interval between the outer peripheral surface and the second guiding surface is set to be When the cable protection tube is wound around the outer circumference, the cable protection tube has substantially the same outer dimension in the radial direction of the outer circumferential surface. The torsion testing machine according to claim 22, wherein a third guiding surface is provided, which is substantially the same as an inner circumferential surface of the cable protection tube when the cable protection tube is bent at the minimum allowable bending diameter. The curvature extends 180 degrees below the lower end of the second guiding surface. The torsion testing machine according to any one of claims 19 to 23, further comprising a reaction force portion that fixes the other end of the object to be tested. A torsion testing machine for imparting a torsional load to a test object by a driving force of a motor, and comprising: a first shaft supported by the bearing to rotate freely around the frame; and a torque sensor via the first shaft And connecting to the motor to measure the torsional load; the second shaft is rotatably supported by the bearing by the bearing; and the chuck is coupled to the torsion sensor via the second shaft for the aforementioned One end of the body is installed. A mechanical testing machine comprising a servo motor and performing mechanical testing using a driving force of the servo motor, the servo motor comprising: a cylindrical motor case for housing a stator and a rotor; and a flange plate formed from the foregoing An opening extending through the rotating shaft of the rotor and fixed to one end of the motor case; and a reaction force plate fixed to the other end of the motor case; the flange plate and the reaction force plate are fixed to the mechanical testing machine On the frame. The mechanical testing machine according to claim 26, wherein a bearing for supporting the rotating shaft is fixed to each of the flange plate and the reaction force plate. The mechanical testing machine of claim 26 or 27, wherein a screw hole is formed in each of the flange plate and the reaction force plate, and the flange plate and the reaction force plate are respectively Screw holes are fixed to the aforementioned frame. The mechanical testing machine according to any one of claims 26 to 28, wherein a first screw hole is formed in the flange plate, the first screw hole is for fixing the servo motor, and The rotation axes of the aforementioned servo motors are parallel. The mechanical testing machine according to any one of claims 26 to 29, wherein a second screw hole is formed in the flange plate, the second screw hole is for fixing the servo motor, and The axes parallel to the aforementioned servo motor rotation axes are orthogonal. The mechanical testing machine according to any one of claims 26 to 30, wherein a third screw hole is formed in the reaction force plate, and the third screw hole is used for fixing the servo motor, and The axes parallel to the aforementioned servo motor rotation axes are orthogonal. The mechanical testing machine according to any one of claims 26 to 31, wherein a fourth screw hole is formed in the reaction plate, and the fourth screw hole is used for fixing the servo motor, and The rotation axes of the aforementioned servo motors are parallel. The mechanical testing machine according to any one of claims 26 to 32, wherein the servo motor further includes a motor cover covering the motor casing, and the motor cover is at both ends of the rotating shaft direction. Covering the side surfaces of the flange plate and the reaction force plate, and joining the side surfaces, and forming a second screw hole for fixing the servo motor on a side surface of at least one of the flange plate and the reaction force plate At least one end portion of the motor cover in the rotation axis direction is formed with a notch portion, and the second screw hole and its periphery are exposed. The mechanical testing machine according to claim 33, wherein a ventilation port is formed in the motor cover, and the mechanical testing machine further includes a ventilation fan installed in the ventilation port. The notch portion extends to the inner side in the direction of the rotation axis of the flange plate or the reaction force plate, and is connected to an inner space and an outer space formed between the motor case and the motor cover. The mechanical testing machine according to any one of claims 26 to 34, wherein the flange plate is fixed to the motor case by three or more pairs of bolts symmetrically arranged on the rotating shaft. One end. The mechanical testing machine of claim 35, wherein the plurality of pairs of bolts are disposed on concentric circles centered on the rotating shaft. The mechanical testing machine according to claim 35 or claim 36, wherein the cross-sectional shape of the motor case is formed into a substantially square shape, and the plurality of pairs of bolts comprise two pairs symmetrically arranged on one of the diagonal lines of the square. bolt. The mechanical testing machine according to any one of claims 10 to 37, wherein the flange plate is fixed to the motor case by 8 bolts symmetrically arranged on a diagonal line of the square. One end. A mechanical testing machine according to any one of claims 26 to 38, which is a torsion testing machine. The mechanical testing machine according to any one of claims 26 to 39, wherein the output of the servo motor is 10 kW or more.