TW200902971A - Universal testing machine, linear actuator and torsion testing machine - Google Patents

Abstract

In a general-purpose test device and a linear actuator which drive a cross head by a servo motor and a feed screw mechanism, the servo motor and a linear guide of the feed screw mechanism are fixed to a single support plate. It is preferable that a drive shaft of the servo motor be coupled to the feed screw by a rigid coupling or a semi-rigid coupling. Moreover, in a twist test device which applies a twist load to a test piece by the servo motor and a speed reduction mechanism, both of the servo motor and the speed reduction mechanism are fixed to a first support member as a single member. It is preferable that a drive shaft of the servo motor be coupled to an input shaft of the speed reduction mechanism by the rigid coupling or the semi-rigid coupling.

Description

200902971 IX. INSTRUCTIONS: TECHNICAL FIELD The present invention relates to a universal testing machine, a linear driver and a torque testing machine suitable for the universal testing machine. [Prior Art] Conventionally, in order to evaluate the strength and rigidity of materials and structures, a material testing machine for applying tensile, compressive, and/or bending stress to materials or the like has been used. This type of material testing machine is generally referred to as a universal test machine. A general-purpose test machine is described, for example, in a machine that is described in Japanese Laid-Open Patent Publication No. 2003-106965 and Japanese Patent Laid-Open No. 2003-90786 (both incorporated herein by reference). The universal testing machine described in Japanese Laid-Open Patent Publication No. 2003-106965 and Japanese Patent Laid-Open No. 2003-90786 has a fixing portion fixed to the machine frame, and can move in a specified direction (upward direction) to the machine frame. A crosshead formed by the ground and a driving device for moving the crosshead. The tensile test is to fix one end of the test piece to the fixed portion and the other end to the crosshead, by driving the crosshead in a direction away from the fixed portion. Further, the compression test is performed by driving the crosshead close to the fixed portion in a state where the crosshead and the fixed portion sandwich the test piece. The bending test is performed by supporting the test piece at one of two points of the fixed portion or the crosshead, supporting the test piece at the other point, and driving the crosshead in a manner close to the fixed portion (three-point bending test). For example, there is an electric linear actuator that is described in Japanese Laid-Open Patent Publication No. 2003-106965, and a hydraulic linear actuator described in Japanese Laid-Open Patent Publication No. 2003-90786. The test machine system using the hydraulic linear actuator constitutes a cylinder that is coupled to the crosshead by using a pump to feed the high-pressure working oil into the cylinder, or by removing the cylinder from the cylinder. For example, the hydraulic linear actuator is driven directly by the hydraulic cylinder to have a small reaction delay, and the vibration wave can be easily oscillated with high hopeful vibrations. The fatigue test can be performed in a short time. On the other hand, the test machine of the hydraulic type linear drive 在 has the use of the surrounding environment due to no leakage and oil mist, and the operation of the oil sump causes the equipment to be enlarged, and the operator is regularly repaired and the working oil is replaced. The cost increases and the consumption of natural resources and the noise generated by the pump.

The electric linear actuator is described, for example, in Japanese Patent Laid-Open No. 2: 〇 3_'. The fine feed screw mechanism produced by 6965. Because the feed screw machine can load large loads and accurately move the drive object, other electric drives 11 (using linear motors and rack and pinion mechanisms) are suitable for general-purpose test machines. The electric linear drive of the second drive mechanism can drive the M-type motor and the feed screw model, so it can be said that it requires a working oil tank and the burden of the environment! ^ The test bench of the drive is compared to the ring around the machine. , s, Lu Yun cost, and test machine miniaturization, etc. have excellent rigidity ^ external system in order to evaluate the strength around the specified shaft of the long strip member, torsion test gas side = generation universal test machine, and use the torque test machine station. The surrounding torque is supported at both ends by a test piece, and a support shaft is applied at one end. Such a torque test machine has a machine. 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 。 Support member (plate member that expands in the vertical direction). A chuck for holding the test piece at both ends is mounted in each of the support members. The chuck attached to one of the support members is coupled to the drive shaft of the servo motor via a speed reduction mechanism and a coupler. Further, the chuck attached to the other supporting member is integrated with the supporting member, and is fixed to the other supporting member by holding one end of the test piece. Therefore, by driving the servo motor, the test piece held by the chuck can be twisted. In general, the servo motor is adapted to rotate the drive shaft with low torque and high speed. In addition, in the torque test machine, the test piece must be twisted at a high torque and at a lower speed. Therefore, in the torque test machine using the servo motor, a speed reduction mechanism such as a worm wheel can be provided between the drive shaft of the servo motor and the chuck to perform a high torque torque test using the servo motor. A test that is generally performed using the above-described universal test machine and torque test machine, such as fatigue test. In the so-called fatigue test, the load (strain) is applied repeatedly on the test piece, and the number of cycles until the test piece is broken is measured. In such a fatigue test, in order to complete the test in a short time, it is necessary to increase the cycle time of the repeated load per unit time as much as possible [Inventive content] (Problems to be solved by the invention) As described above, the universal test using the feed screw mechanism The machine needs to connect the drive shaft of the servo motor with the feed screw. Similarly, the torque test machine needs to couple the drive shaft of the servo motor with the input shaft of the speed reduction mechanism. In general, when coupling the input shaft of the feed screw or reduction mechanism to the drive shaft of the servo motor, it is necessary to accurately position the two axes of the coupling (set 7 200902971 hearts). However, when it is produced by the usual processing error, the servo and the combination precision (such as ±1〇〇μηι) can be made of a highly rigid material between the drive shaft and the feed screw which are not negligible. Just two (, heart or declination). Therefore, in the case of large bending stress, and without the coupling, the two axes of the coupling, the shaft on the shaft smoothly spins the soap. Because ❿, 弁 _ feed screw And the engine platform of the speed reduction mechanism 'by the absorbable test machine or the force to move the drive shaft. Soft two == wheel and shaft feeding the aforementioned f-bend stress, and the joint can be made by the elastic body J Rotate and sleekly convey the == coupling, so except for f:; = : by, body, torque. Use soft couplings to absorb some degree of J, and rotate back and forth with high cycle When the coupling f is not too high, the coupling cannot follow the wheel into the shaft 4 』= When turning, the output shaft cannot be rotated back and forth in a high cycle, and the wheel is fine. This is common to the electric servo motor and t-turn. In the test machine, the test piece cannot be applied in a high cycle. Use the feed two correct universal test machine to perform the fatigue test in a short time. This type of test machine uses the universal test machine of the hydraulic drive mechanism. Similarly, the test can only be connected to the test. However, the motor====================================================================================================== The combination, by using high rigidity, the knotter, can apply the load to the test piece at a high repetitive speed = test machine, torque test machine, and electric drive that can be applied to such a universal test machine: In the above problem, the universal test machine and the drive of the present invention have a servo motor and a linear guide fixed on the support plate: the servo motor and the linear guide use the support plate as a reference, and the straight two are mounted on the support plate, The component is positioned with relatively high precision, and the position accuracy is easy. In addition, the torque testing machine of the present invention has a frame, which is fixed on the base of the machine; a motor; a speed reduction mechanism; a coupling shaft of the coupling mechanism of the speed reduction mechanism and a driving portion of the servo motor, which is held at one end of the output shaft of the speed reduction mechanism, and the second holding portion. It is fixed to the frame of the test = the other end; and the first support member is fixed to the frame, the fixed servo motor and the speed reduction mechanism. Thereby, the servo is mounted by using the first support as a reference The motor and the speed reduction mechanism are easy to ensure the accuracy of the member 2. [Embodiment] = The following is a detailed description of the embodiment of the present invention, which is a general testing machine of the first embodiment of the present invention. As shown in the first figure, the test machine table i of the present embodiment is provided with the machine frame portion 10 fixed to the base B, and the upper end of the test piece (or the upper portion of the test piece). The fixed portion 2A that abuts and the moving portion 30 that abuts against the lower portion of the test piece (or the missing piece attached to the lower portion of the test piece). ', 9 200902971 In the present embodiment, the machine frame 10 has a pair of leg portions 11 extending upward from a substantially vertical direction of the base B, and a pair of guides extending upward from a substantially vertical direction of the upper ends of the leg portions 11 The rod 12 and the top portion 13 are provided in such a manner as to join the upper ends of the two guide rods 12. A through hole 13a is provided in a schematic central portion of the top portion 13. The feed screw 22 for moving the fixing portion 20 in the vertical direction is inserted into the through hole 13a. A nut 23a that engages with the feed screw 22 is provided above the top portion 13. Reference numeral 24a is a radial ball bearing for rotatably supporting the nut 23a. Further, the outer ring of the radial ball bearing 24a is fitted to the bearing support portion 24b fixed to the upper portion 13 by a bolt (not shown), and the two are integrally formed. Similarly, the nut 23a is fitted into the inner ring of the radial ball bearing 24a and the two are integrated. Therefore, the nut 23a can rotate the bearing support portion 24b, but cannot move in the downward direction and the radial direction of the nut 23a. Therefore, when the nut 23a is rotated, the feed screw 22 engaged with the nut 23a moves in the vertical direction. A motor 25 for driving the nut 23a is disposed above the top portion 13. The drive shaft 25a of the motor 25 is housed in the gear case 26. The gear case 26 has a member for decelerating the rotation of the input shaft (the drive shaft 25a of the motor 25) and transmitting it to the well-known gear mechanism of the output shaft 26a. As shown in the first figure, the output shaft of the gear case 26 extends vertically downward from the lower end of the gear case 26. That is, the gear case 26 has a function of converting the rotational motion of the drive shaft 25a extending in the horizontal direction into the rotational motion of the output shaft 26a extending in the vertical direction. A drive pulley 26b is mounted on the output shaft 26a of the gear case 26. Further, a driven pulley 23b is attached to the nut 23a. The endless belt 27 is erected on the drive pulley 26b and the driven pulley 23b, and the rotation of the drive pulley 26b is transmitted to the driven pulley 200902971 23b via the endless belt 27. Therefore, by rotating the drive shaft 25a of the motor 25 by the drive motor 25, the nut 23a can be rotated and the feed screw 22 can be moved up and down. The upper stage 21 of the fixing portion 2 is suspended at the lower end of the feed screw 22. In the upper and lower ends of the upper stage 21, a through hole 2U extending in the upper direction is formed. A guide rod 12 is inserted into the through hole 21a. Therefore, the moving direction of the upper stage 21 is limited only to the upper and lower sides. Bolt holes 21b that are perforated in the horizontal direction (the direction from the front surface to the back surface in the drawing) are formed at both ends in the right and left directions of the upper stage of the fixing portion 20 (the position outside the through hole 21a). The side surface of the through hole 21 & is enlarged to the outside in the left-right direction in the figure of the upper stage 21, and the slotted long hole orthogonal to the bolt hole 21b is formed in the upper stage 21, and is not shown in the figure - Show. Therefore, when the screw hole m is inserted into the screw hole m and tightened, the diameter of the through hole 21a becomes small, and the inner peripheral surface of the through hole 爽 cools the guide rod I2. As a result, the upper stage is fixed to the guide. Further, when the bolt 21c is loosened from this state, the motor can be driven and the stage 21 can be moved up and down. - The mechanism for performing the up-and-down movement and the fixing of the upper stage 21 as described above is used in response to the test piece. The distance from the movable portion 30. In addition, the test: and the rumor is only supported by the guide rod 12, the load of the test occurs 23a, also to the ball bearing - and the shaft 1

When the weight of the upper load "1" is U and the distance between the crystals and the second is small, although the feed screw can be accurately driven, the strength of the non-knife is lowered. However, in this embodiment, since the weight of the upper stage 21 is significantly exceeded The load is not applied to the feed screw and ^200902971 mother, so the request, ^ HI 20 fish small feed screw and nut, can accurately adjust the solid 疋 '20 and can be, the interval between the 3 。. The yak 28 is installed during the tensile test. The load sensor (10) σ is included in the attachment 28 to measure the load applied to the test piece at the time of the test. The other two load: 21 2 special sensation as a separate component from the attachment, It can also be installed on the upper = install load sensor, and then attach the attachment 28 to the lower part of the load sensor. ^'ATm 0 f Connect and fix the workbench 33. Fig.: U above the U.下 认 认 , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , 'Workbench work...it, first picture.) When testing, _added to ^^ _ plate, and under κ under the table 33, the load by tt3G is substantially regarded as a rigid body. The motor 35 is attached to the frame 37, and the AC has a plurality of ribs 37a. The upper end of the side wall forming 37a of the support frame 37 is offset from the table by the motor support frame 37 and the rib motor support frame 37. The "face 2 welding" table 33 and the motor 35 are integrated into the present invention. . In addition, the AC servo output AC servo motor can select the high and low internal inertia of the reverse speed, which can greatly reduce the rotary motion of the 9th/previous AC servo motor. A repetition rate of 500 Hz is established to drive the drive shaft. Further, a lower stage 31 which is configured to be movable in the vertical direction by the AC ship motor 12 200902971 35 is disposed on the table top. A ball screw 36 and a linear guide 4 that are coupled to the drive shaft 35a of the Ac servo motor 35 via the rigid coupling 34 via the lower stage 31 constitute a feed screw mechanism. The linear guide is an element that guides the movement direction j of the lower stage 31 to the upper and lower directions. The linear guide 4 has a guide frame 42, a pair of obstructions 44, and a moving block 牝. The guide frame is fixed to the upper surface 33c of the table 33 by bolts or the like. The guide frame 42 is in the vertical direction, the pair of side walls 42a, and the upper end side wall 42a upper wall surface 42b are all inverted. In the shape 42a, the 4 series extends in the vertical direction of the track, and is smaller than the side wall. In addition, each of the moving blocks 46 is fixed to the left and right ends of the lower part of the center, and the corresponding track 44 is: The movement of 46 is guided by the obstruction 44. Therefore, the moving direction of the load port 31 is limited to the up and down direction. The J I3 carrier 31 is embedded in the upper part of the ball screw machine 36 by the ball screw machine. The snail; the dry part of the t screw: the mother 4? is formed on the ball 31 by the linear guide 4 〇 guide: said, because the lower stage thus makes the ball, 6 two; 'with the ball screw nut called - The opening portion 42c has an upper end of the opening 42c. The lower stage 31 penetrates the upper side of the 42b. Therefore, the lower core is more than the attachment 28 of the upper wall surface stage 21 and is mounted on the upper side. During the tensile test, the test piece is mounted on the ten via the 200902971 chuck. Further, in the compression and bending test, the test piece or the jig is placed on the crosshead 31b. The lower portion of the ball screw 36 becomes the shaft portion 36b which is not formed to be engaged with the ball screw nut 31a. The shaft portion 36b is coupled to the drive shaft 35a of the AC servo motor 35 via the rigid coupling 34. The rigid coupling 34 of the present embodiment is formed around the shaft portion 36b of the ball screw 36 (i.e., the drive of the AC servo motor 35). The torque around the shaft 35a is extremely high, and the torque applied to the AC servomotor or the drive shaft 35a can be transmitted to the ball screw 36 with high reactivity, but the details are as follows. - Secondly, the order is! The structure of the device 34 is shown in an enlarged cross-sectional view showing the rigid coupling 34 and the fine Yamaguchi AC clothing motor f, = 34 and the coupling 36b. The axis of the shaft and the shaft of the ball screw 36 are medium-sized. That is, the cylindrical body 3Π, that is, the cylinder having a stepped thickness). The upper portion of the shaft portion 36b W is opened D, A. The upper portion of the ball screw 36 is inserted from above, and the upper portion of the AC servo V^34C is inserted from below. % of the cylinder, and a cylinder with a tear = The diameter of the shaft portion 36b of the lower opening portion of the drive shaft of the drive shaft is as follows: due to the ball screw 36, the upper cylinder; 34 = the service horse, the movement of 35 is small. The drive shaft 35at t-axis/na of the other cylindrical portion, the lower portion, and the lower cylindrical portion 35 are substantially equal to the outer diameter of the lower cylindrical portion 34b, and the AC servo motor is substantially equal to the lower cylindrical portion 34b. Therefore, in the narrow portion 20000221 and The shaft portion 36b of the ball screw 36 and the drive shaft 35a of the AC servo motor 35 are in a state in which the inner peripheral surface of the ball and the shaft portion 36b of the ball screw 36 and the outer circumference of the drive shaft 35a of the AC servo motor 35 have almost no gap. It is accommodated in the narrow portions 34e and 34f. The diameters of the upper opening portion 34c and the lower opening portion 34d are larger than the outer positions of the shaft portion 36b of the ball screw 36 and the drive shaft of the AC servo motor 35, respectively. In order to fix the upper opening portion 34c and the lower opening portion 34d to the shaft portion 3 of the ball screw 36 and the drive shaft 35a' of the Ac servo motor 35, the fixing ring and the 14'' are used. The fixing ring 130 has an inner wheel 132, an outer wheel 134, and a bolt 136. The outer peripheral surface 132a of the inner ring 132 has a tapered surface whose diameter is reduced downward. The inner peripheral surface of the second surface is a cylindrical surface slightly larger than the outer diameter of the shaft portion 36b of the ball screw 36. The inner wheel is made up of a flange portion 1 that is enlarged to the outside in the radial direction. A plurality of flange portions mc are inserted in the vertical direction, $,

In addition, the inner circumferential surface of the outer wheel m is 13 =:, and the screw is the surface. The inner peripheral surface 134 of the outer wheel W = the taper angle (10) having the same diameter as the diameter becomes smaller. Further, the inner circumferential surface of the inner wheel I% is slightly smaller than the diameter of the upper opening portion 34c, and the outer circumferential surface 134b is formed to correspond to the bolt hole 132d to open the meat surface. Furthermore, the outer wheel 134 is combined with the female thread 134c. In addition, there are a plurality of outer diameters (maximum diameters) which are smaller than the inner circumference* 134a of the inner wheel 132'134. Therefore, when the upper end of the U inner peripheral surface (10) is placed directly on the outer ring U4, the inner wheel surface is grounded, the inner wheel 132 is formed on the lower surface of the flange portion which is not in contact with the upper surface of the outer wheel 134, and the inner wheel U2 is inserted into the upper portion. The state in which the opening is raised. When the gap between the outer wheels 134_ is tightened through the bolt holes 132d of the shaft C and the shaft portion depth #132c of the ball screw 36, and the bolt 136 of the female thread 134c is inserted into the bolt 136, the tapered surface 132b of the inner wheel 132 is from the outer wheel 134. The tapered surface 134a receives a force inward in the radial direction, and the cylindrical surface 132b of the inner ring 132 strongly presses the shaft portion 36b of the ball screw 36. Further, at this time, the tapered surface 134a of the outer ring 134 receives a force directed outward in the radial direction from the tapered surface 132b of the inner ring 132, and the cylindrical surface 134b strongly presses the upper opening portion 34c. The shaft portion 36b of the ball screw 36 is firmly fixed to the upper cylindrical portion 34a of the tubular body 34B by the static friction generated by the result, and the two are integrated. Further, the two sets of the bolts 136, the bolt holes 132d, and the female threads 134c are respectively shown in the drawing, but actually, a plurality of (e.g., 10 sets) are provided on the circumference centering on the axis of the ball screw 36. Similarly, the fixing ring 140 has an inner wheel 142, an outer wheel 144, and a bolt 146. The outer peripheral surface 142a of the inner ring 142 has a tapered surface whose diameter is increased upward. Further, the inner circumferential surface 142b of the inner ring 142 is a cylindrical surface having a slightly larger outer diameter of the drive shaft 35a of the AC servo motor 35. A flange portion 142c enlarged in the radial direction outer side is formed at the lower end of the inner ring 142. A plurality of bolt holes 142d through which the bolts 146 are inserted in the vertical direction are provided in the flange portion 142c. The inner circumferential surface 144a of the outer ring 144 becomes a tapered surface whose diameter becomes smaller. Further, the outer circumferential surface 144b of the outer ring 144 is a cylindrical surface slightly smaller than the diameter of the lower opening portion 34d. Further, in the outer ring 144, a plurality of female threads 144c engaged with the bolts 146 are formed corresponding to the bolt holes 142d. Further, the diameter (maximum diameter) of the lower end of the inner circumferential surface 144a of the outer ring 144 is smaller than the diameter (maximum diameter) of the lower end of the inner circumferential surface 142b of the inner ring 142. Therefore, when the tapered surfaces are placed in contact with each other and the inner ring 142 is placed below the outer ring 144, the upper surface of the flange portion 142c of the inner ring 142 is in a state of being floated without coming into contact with the lower surface of the outer ring 144. The outer wheel 144 and the inner wheel 142 are inserted into the lower opening portion 34d and the AC servo motor 35 16 200902971 === the force of the inner wheel 142 when the ferrule 146 is 146 from the outer wheel through the flange portion of the flange portion. The 144a is driven by a drive shaft 35a with a radial direction toward 35. The cone is strongly pressed from the servo motor from the inner wheel 142. In addition, the drive shaft 35a of the tapered surface 144a of the outer wheel 144 is used by 4=:"4d . The AC servo motor is %. In addition, in the figure, the 夂-夂 邛 , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , , "The center of the circumference is provided with a plurality of thick upper ground cylindrical portions and lower cylindrical portions 34b rigid and rolled: Thus, the torque of the joint portion of the rigid coupling 34 is equal to: f and the drive shaft 35a of the AC servo motor 35 = Therefore, the rigid coupling 34 can highly transmit the torque of the drive shaft of 3 = 35 to 35 balls to the ball as shown in the second figure, at the center of the work 纟 33 A through-hole bead screw 36 is provided through the through hole 33d. In the present embodiment, the hoisting screw 36 is received at a position of the through hole 33d in order to receive the hoisting screw 36 of the large load in the thrust direction in the rotatable branch. The following is a description of the construction of the vehicle. The fourth drawing is a longitudinal plan view of the vicinity of the through hole 33d of the table 33. As shown in the figure, a first bearing mounting member 152 having an annular shape is fitted into the through hole 33d. At the upper end of the first bearing mounting member 152, a flange portion 152a which is enlarged to the outer side in the radial direction is formed. The flange portion 152 is provided with a through hole 152b that is perforated in the vertical direction. A female screw 33e is formed on the table 33 at a position corresponding to the through hole 152b. By inserting the bolt 158 = into the through hole 152b and the female thread 33e, and secondly tightening the thread 158a, the first bearing mounting member 152 is fixed to the table phantom, and the two form an integral C5. Further 'the screw at the ball screw 36 There is a shaft between the portion 36a and the shaft portion 36b. The straight edge of the 卩36b side becomes smaller. There is a first collar 154 between the steps. Then, under the first collar 154, the combination of the corner bearing 丨5丨 and the second collar 155 °, in addition, a male thread is formed in the middle of the shaft portion 36b of the ball screw 36, which will be the first Ring 1 =, the combined angular ball bearing 151 and the second collar 155 are inserted into the shaft portion 36b of the ball screw 36, and the first collar is placed on the male thread 36c' of the ball screw cup 36 by the nut 156. The inner wheel of the combined angular ball bearing 151 is supported between the 154 and the second collar 155. Further, a second female member, member 153, is disposed under the first bearing mounting member 152. The second bearing mounting member 153 is fixed to the first bearing mounting member 152 by bolting. The front surface of each of the second bearing mounting combined angular ball bearings 151 is integrally assembled (the upper surface of the 153 abuts against the outer wheel of the combined angular ball bearing 151, and the outer wheel of the combined angular ball bearing 151 is supported from below. Diagonal ball bearing 151a, subjected to a large load in the upward direction during tensile testing, at pressure

Angular ball bearing, city In this embodiment, luxury (front combination). In this embodiment, the second load is a large load. Therefore, the thrust load can be supported in the upper and lower directions by combining a pair of positive and negative (combining the back faces). In particular, the combined angular ball bearing 151, 200902971 with the front combination can prevent the shaft (the internal Jf force of the ball screw 36; in the middle of the bearing, the bearing itself does not have the friction of the ball and the inner and outer wheels of the wheel bearing, but the supply is adjusted. The oil bearing 151 oil leaks out, and the gap between the first ring 154 and the second ring is the second ring; the clearance between the two members (5) is respectively provided with oil seal, 1571 ). ^Loading f 153 lubricating oil from the first bearing mounting member 152 and two to prevent

A gap 159 is provided between the 154 and the mounting member 154. In addition, the bearing member 153 of the Didi factory is formed with a transverse bearing extending in the radial direction; 5 = when the oil is supplied from the outside: usually by the second, the orbit of the linear guide 4 of the present embodiment The composition of 44 and block 46 (second figure) will be described in detail using the drawings. The fifth system is on the one side (i.e., the horizontal plane) perpendicular to the long axis direction of the track 44. The cross-sectional view of the cut track 44 and the moving block 46 is shown in the sixth figure as a cross-sectional view of the fifth figure. As shown in the fifth and sixth figures, the moving block 40 is formed with a recess to surround the rail 44, and four recesses 46a, 46a extending in the axial direction of the lane 44 are formed in the recess. The grooves 46a and 46a accommodate a plurality of balls 46b made of stainless steel. In the rail 44, a position 44' opposite to the groove 46a, 46a' of the moving block 46 is provided with a groove 44a, 44a, respectively, and the ball 46b is sandwiched between the groove 46a and the groove 44a, or between the groove 46a and the groove 44a. . The grooves 46a, 46a', 44a, and 44a' have a circular arc shape in cross section, and the radius of curvature is substantially equal to the radius of the balls 46b. Therefore, the balls 46b are in close contact with the grooves 46a, 46a, 44a, 44a in a state where there is almost no play. Inside the moving block 46, there are 4 19 200902971 exit paths & 46c, 46c which are substantially parallel to the respective grooves 46a. As shown in the sixth figure, the two ends of the groove and the exit path 46c are connected by a U-shaped path, and the groove 46a, the groove 44a, the exit path 46c, and the u-shaped path are offset to form the ball 46b for circulation. The loop path. The same circulation path is also formed by the grooves 4 such as, the grooves 4, and the exit path 46c. Therefore, when the moving block 46 moves to the lane 44, the plurality of balls 4 are still rotated in the grooves 46a, 46a, 44a, 44a to circulate in the circulation path. Therefore, even if a large load is applied in a direction other than the direction of the axis of the road, since the moving block can be supported by a plurality of balls and is held by the rotation of the balls 46b to reduce the resistance in the direction of the track axis, the moving block 46 can be made to the track. 44 moves smoothly. Further, the inner diameter of the exit path 46c and the u-shaped path 46d is slightly larger than the diameter of the ball 46b. Therefore, the frictional force generated between the exit path 46c and the U-shaped path 46d and the ball 46b is extremely small, thereby preventing the circulation of the balls 46b. As shown in the figure, the contact angle between the rows of the two rows of balls 46b sandwiched by the grooves 46a and 44a is ±45. The front combined angular ball bearing. At this time, the contacts of the contact angle grooves 46a and 44a are in contact with the balls 46b, and the radial direction of the linear guide (from the moving block to the track, in the lower direction of the fifth figure) The angle of formation. The angular ball bearing thus formed can support the reverse radial direction (the direction from the track to the moving block, the upper direction in the fifth figure) and the lateral direction (the direction orthogonal to both the radial direction and the direction of the moving block = the retreating direction) The negative direction of the 'left-right direction in the fifth figure' is similarly formed by the groove 46a, and the row of the balls 46b of the two rows sandwiched by 44a (the grooves 46a, 44a, and the contact points of the balls 46b) The connection 'the angle formed by the reverse radial direction of the linear guide rails' is roughly ±45. The front combined angular ball bearing. The angular ball bearing can support 20 200902971 to support the radial direction and the lateral direction. Further, the row of the balls 46b of the two rows which are sandwiched by one of the grooves 46a and 44a (the left side in the drawing) and one of the grooves 46a and 44a' (the left side in the drawing) also form a front combined type angular ball bearing. Similarly, the rows of the balls 46b of the other row (the right side in the figure) of the groove 46& and 44a (the right side in the figure) and the groove 46a, and the other side (the right side in the figure) of 44a are also formed into a front combination type. Angular ball bearings. As described above, in the present embodiment, the front side combined type angular ball bearing having a plurality of balls 46b is supported by the load acting in the radial direction, the reverse radial direction, and the lateral direction, respectively, and can be sufficiently supported to be applied to the track axis direction. Large load in the direction of the outside. Next, the configuration of the control measuring unit of the universal testing machine 1 of the present embodiment will be described. The seventh diagram is a block diagram of the control measuring unit 200 of the universal test machine i of the present embodiment. The universal test machine ι of this embodiment can perform the fatigue test in a short time, and can apply the reverse load on the test piece in a short cycle. The control measurement unit 200 of the universal test machine 1 has a set value indicating unit 210, a drive control unit 22, and a measuring unit 25A. The threshold value indicating unit 210 is a unit for indicating how to move the lower stage 31 (first map). Specifically, the displacement amount (target position) of the lower stage 31 from the initial position is output as a signal, and is transmitted to the unit of the drive control unit 220. The set value indicating unit has an input interface 212 and a waveform generating circuit 214. The input interface 212 is for connecting the interface of the set value indicating unit 21 and the workstation (not shown). The operator of the universal test machine 1 operates the station and instructs how to displace the lower stage 31. If the static bear tensile test is performed, the operator operates the workstation, inputs the displacement speed applied to the lower load Δ 21 200902971 31, and sends it to the input interface 212. Further, when performing a fatigue test in which a reverse load is applied to the test piece, the operator operates the work station, inputs the amplitude, frequency, and waveform of the lower stage 31 (using a waveform of a sine wave or a triangular wave, etc.), and transmits it to the input interface 212. The indication input to the input interface 212 is passed to the waveform generation circuit 214. The waveform generating circuit 214 interprets the indication sent from the input interface 212, successively calculates the amount of displacement of the lower stage 31 from the initial position, and sends it to the drive control unit 220. Further, when performing the fatigue test, the lower stage 31 is not limited to being driven by a constant waveform or frequency of a single sine wave or a triangular wave, and the lower stage 31 may be driven by a function synthesized from functions having various amplitudes or frequencies. The lower stage 31 can be driven with the amplitude of the lower stage 31 as a function of time, as a function of multiplying the sine waves of different frequencies. The displacement amount of the lower stage 31 is output from the waveform generating circuit 214 as a digital signal. Thus, the signal sent from the waveform generating circuit 214 to the drive control unit 220 is first input to the D/A converter 222 and converted into an analog signal. Next, the amount of displacement information converted to the lower stage stage 31 of the analog signal is transmitted to the amplifier 224. Then, the amplifier 224 expands and outputs the displacement amount information transmitted from the D/A converter 222 to the lower stage 31. As described above, in the present embodiment, the AC servo motor 35 performs various tests by driving the lower stage 31. Here, the AC servo motor 35 incorporates an encoder for detecting the number of revolutions of the drive shaft 35a (first figure), and the number of revolutions detected by the encoder is sent to the current position operation circuit 226 of the drive control unit 220. The position calculating circuit 22 6 calculates the current position of the lower stage 31 based on the detection result of the encoder of the A C servo motor 35, and outputs it. 22 200902971 Then, the difference between the round-out of the amplifier 224 and the current bit output (that is, the signal corresponding to the difference between the positions of the lower-loaded A-reverse circuit 226) is sent to the target position of the thunder, and 31. The power 々 IL generating circuit 228. The current generating circuit 228 is based on

The sorrow of the sorrow is like a thunder. The machine is owed to the machine, and the two-phase current of the servo motor 35 is generated, and the wheel and the AC output are driven to the AC servo motor 35, and the motor is eclipsed. position. The lower stage 31 is caused to reach the target by driving the lower stage 31 to apply the bridge circuit 256 from the accessory 28 built in the universal test machine 1, the load susceptor 254, and the load sensor 254 = load transfer. To detect. l ^λ News to the workstation. The workstation statistics are sent from the round. If the time _ is taken as the horizontal axis, it will be applied to the test piece and the vertical axis. Heart for

The value is transferred to the load of the output of the waveform generating electric= 258, and the so-called feedback control which changes the displacement action of the lower stage 31 in response to the load is obtained. When the displacement ink and the load value of the following stage 31 are not in the JL ratio relationship, that is, when the test piece is lifted and lowered, the amplitude of the lower stage or the like can be controlled. By using the universal test machine 1 composed of one or more, the static break test and the fatigue test of the test piece can be performed. Here, in the present embodiment, the lower stage 31 is driven by the AC servo motor 35 having high reactivity and high torque. Therefore, the universal test machine can apply a maximum of several hundred to 1^ to the test piece, and a reverse load can be applied to the test piece at a high frequency of several hundred Hz. Therefore, when the universal test machine 1 of the present embodiment is used, the fatigue characteristics of the test piece can be evaluated in a short time, and 23 200902971 ° can be used for a short test time. In order to make t 'take the wealth _ the structure of the slant, field AC ^ ^ SS, ct second move S in the same movement, : = use 3 ^ two use; = servo motor - heart ^ 35a and ball screw 36 35 drive shaft ': all on the same - board surface:: accuracy centering. In addition, the 'inclined position. When the composition of the present embodiment is used, the operation of the present embodiment is based on the fact that the AC servo motor is shipped for a high degree of accuracy, so the effect is due to the centering error ^ ^ And the drive shaft of the ball screw 36 and the drive shaft of the ball screw 36: the servo motor and the feed 'torque stress are small. Usually used: (rubber and gold; two devices), the use of a soft coupling through the mediation. In the case of absorbing the bending stress ', it is possible to perform two-axis determination and fineness with high precision. As described above, the rigid coupling C formed by the two materials is used for the purpose of rigidity, and the AC 祠 motor 35 is used. = can be highly reactive to make t 36 (four) 36b. Therefore, even if the torque is transmitted to the drive shaft 35a of the ball 3S to make the AC servo horse follow the drive car up by the mouth of 35a, the second is that the ball screw 36 can still be rigid, and even if it is tested, even if it is tested When the sheet metal is equal to or higher than the speed of the crosshead 3lb back and forth 24 200902971, the set load (strain) can still be correctly applied to the test piece. That is, the universal test machine 1 of the present embodiment can perform the fatigue test of the test piece in a short time. In addition, in the present embodiment, as shown in the second figure, the rail 44 is fixed to the guide frame 42 and the moving block 46 is fixed to the lower stage. However, the moving block can be separately fixed to the guide. The frame is constructed by fixing the rail to the lower stage (that is, the nut that engages with the feed screw). In addition, in the embodiment, the mechanism for moving the cross head of the universal test machine up and down uses a linear driver. However, the linear drive can be used to make the car C up and down in addition to the universal test machine. The vibration tester for the direction excitation is Γ. That is, according to the present embodiment, the linear actuators of the four movable portions 30 and the linear guides 40 (first drawing) are provided, and are respectively fixed to the machine frame portion 10' supported by the base B. Then, the respective crossheads 31b are fixed to the wheels W of the car C, and the car C is excited by the AC servo motor 35 that drives the movable portion 30. This type of vibration test machine can excite a high vibration frequency such as the weight of the vehicle C. Further, in the present embodiment, the rigid coupling 34 couples the shaft portion 36b of the ball screw 36 with the drive shaft 35a of the AC servo motor 35 (third drawing). However, the present invention is not limited to the above configuration, and other couplers having high rigidity in the torque direction may be used. Such a coupler is the semi-rigid coupler of the second embodiment of the present invention which will be described next. A general-purpose test machine in which a ball screw and a drive shaft of an AC servo are coupled by a semi-rigid coupling is described as a second embodiment of the present invention. Further, in the first embodiment and the second embodiment of the present invention, only the coupling of the ball screw and the drive shaft of the AC servo motor is different, and the others are the same. Therefore, in the present embodiment, the same reference numerals as in the first embodiment are given to the members or elements of the same as the first embodiment 25 200902971, and the detailed description thereof will be omitted. The ninth drawing shows an enlarged sectional view of the semi-rigid coupling 3 in the present embodiment, and the drive shaft 35a of the Ac servo motor 35 and the shaft portion 36b of the ball screw 36 which are coupled to each other via the semi-rigid coupling 300. . The semi-rigid coupling 300 of the present embodiment constitutes a very high torque rigidity. The high reactivity makes the torque applied to the drive shafts 3 5 & of the AC servo motor 35 to the ball screw 36. In addition, the displacement of the shaft in the longitudinal direction is softly absorbed by the internal resin member, and the vibration in the axial direction caused by the servo that is transmitted from the drive shaft 35a of the Ac servo motor% is greatly attenuated, and is not easily transmitted to the ball screw. 36. As shown in the ninth figure, the semi-rigid coupling 3 is composed of inner and outer wheels 320 and 340 made of nylon, and a plurality of bolts 382 which are fixed to each other. The inner diameter of the circular hole 362a and the ground circular hole which are interconnected in the center is inserted into the AC without a gap, and the size of the upper drive shaft 35a is the size of the upper drive shaft 35a, and the round hole 362b is 35 into the ball screw 36. The larger diameter of the shaft portion 36b is inserted into the gap. Since the diameter of the shaft portion 36b of the ball screw 36 is smaller than ac = (four), the outer diameter of the circular hole 362b extends beyond the center of the inner circumference of the inner ring 360. The side surfaces 364 and 366 extending from the flange portion 360a are formed as the conforming portions, respectively, at the central portions of the two faces other than the wheel. Conical tapered conical surface that tapers. The top end of the axial direction and the outer diameter of the outer wheel Ia form a through hole of the inner side surface 322, 342 of = 26 200902971, respectively. The outer wheels 320 and 340 are disposed such that the tapered surface opening directions of the inner side surfaces 322, 342 are directed toward the inner side of the inner wheel 36. The tapered inner side surfaces 322, 342 of the outer wheels 320, 340 respectively have the same taper angle 与 as the outer sides 360, 366 of the inner wheel 360, and then the inner side 322 of the outer wheel 320 and the outer side 364 of the inner wheel 36, the outer wheel 340 The inner side surface 342 is overlapped with the outer side surface of the inner wheel 36'. The tapered portion formed in the inner wheel is inserted into the through hole of the outer wheel 320, 34'.

In addition, the female screw 344 engaged with the male screw formed at the distal end portion of the bolt 382 around the through hole of the outer ring 34 is formed at equal intervals on the circumference centering the shaft of the through hole. One. Further, in the flange portion 36A of the outer ring 320 and the inner ring 360, bolt holes 324, 368 are formed at positions corresponding to the female threads 344, respectively. Then, the six screw gauges 382 are inserted into the bolt holes of the outer wheel 32 and the bolt holes 368' of the inner wheel 36 to engage with the female threads 344 of the outer wheel 34. In the round hole 362a of the inner ring 36, the top end of the AC servo motor d is inserted from below, and the hole 362b is inserted from above, and the top end of the shaft portion 36b of the stem 36 is closed. The fastening bolt 382 is strongly sandwiched by the outer wheel 320 and the outer wheel 340 from both sides, and the two tapered portions are deeply embedded in the outer wheel 32〇, 34, the hole, the bird to the feeding motor== the shaft of the screw 36 36b applies a strong side pressure, respectively. Since the round hole 362b and the drive shaft 35a, the ball 蟫浐% * ±, respectively, a strong force is generated between the round hole 362a and the shaft portion 36b of the force generating force, and the wire shafts 35a and 360 are integrally coupled. . As a result, the torsion force 半 of the semi-rigid dry 36 t inner wheel portion is equal to or larger than the ball screw 36 and the t-c servo motor 35. Sexuality # 挂 挂 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在In addition, in semi-rigid joint

The shaft portion of the bead screw 36 = the tip end of the drive shaft 35a of the motor 35 is coupled to the gap of the roller. Therefore, when the tip is slightly small (for example, about 1 mm), the inner wheel 360 is elastic and proud: the interval of the force from the direction in which the motor applies the compression axis is narrow, and in the half of the drive shaft, the margin of the screw can be 113GG (four) (four) direction of force 'in aim The force of the side of the buckle is greatly reduced. In this embodiment, <=. The dynamic attenuation rate is roughly the same in the natural vibration number of the drive shaft 35a, and the vibration in the radial direction of the drive shaft 35a or the radial direction of the shaft can be effectively attenuated. Further, as described above, the distance between the top of the drive shaft 35a of the AC feeding motor 35 and the tip end of the shaft portion 36b of the ball screw #36 is as short as 1 mm, and the entire circumference of the top end of each shaft is integrated with the inner wheel. . Therefore, the rotational driving of the drive shaft 35a of the AC servo motor 35 can be accurately transmitted to the ball screw 36 by being sufficiently rigidly coupled in the return direction. The first and second embodiments of the present invention described above relate to a general-purpose test machine using a feed screw mechanism. However, the present invention can be applied to other types of material testing machines of the third embodiment of the present invention described below in addition to the general testing machine. Fig. 10 is a front view of a torque testing machine of a third embodiment of the present invention. Further, the figure is a top view of the torque test machine of the present embodiment. In the torque testing machine 501 of the present embodiment, the long test piece S is subjected to a torque test in a state where the longitudinal ends of the test pieces S are held horizontally by the claws 572a and 547a of the chucks 572 and 574 at both ends. In addition, in order to clarify the configuration of the torque testing machine 501, the test piece s and the chucks 572, 574 of the test piece 2009, 200902971 = test pieces are only shown in the tenth figure. That is, a plan view of the torque test type 5 machine 501 in which the test piece s and the chucks 572, 574 are removed is shown. In the present embodiment, in the present embodiment, it is fixed on the base B ("two:, 510 is provided with: an end piece $p (five) fixed end support portion 520 for fixing the supporting test piece S, And a driving end support portion 530 that rotatably supports the test pull i to the other end (drive end). Then, the i-measuring end support portion 53G breaks the specified torque of the circumference, and can apply a torsional stress on the test piece S. The F-buckle end support portion 52G has a mounting flange 527 which is used for the end of the clamp end of the test piece S. The mounting end is fixed from the +27 On the opposite side of the face of the end side chuck 572, the support shaft 526 extends in a substantially horizontal direction. The 562 is coupled to the load sensor for torque measurement at the top end of the 526. At the top end of the support shaft 526 and the load sensor 562 The edge is formed with a convex 'edge' for connecting by fixing each of the tenon shafts 526 and the load cell 562 by bolts. The load sensor handle is fixed to the side of the fixed end side of the fixed end support portion 520. 2 L side frame 522 is fixed to the fixed end of the fixed end support portion 520 by means of bolt fixing, welding, or the like. The plate 521. The fixed end support plate 521 0 is fixed to the lower frame 51. Here, the frame 522 is a plate-like member having an L-shaped cross-sectional shape, and a reinforcing rib 522a is formed in the base portion. Therefore, the side frame 522 = is rigid. Since the fixed end support plate 521 is strongly fixed to the lower eucalyptus 510, the side frame 522 can be regarded as a rigid body integral with the base b, but will be described later in detail. The fixed end of the sheet S is fixed to the side frame 522 via the fixed end side chuck 572, 29 200902971 mounting flange 527, the support shaft 526, and the load sensor 562. Here, the fixed end side chuck 572, the mounting flange 527, and the support The shaft 526 and the load sensor 562 sufficiently increase the torsional rigidity of the test piece S, and by applying a torque to the driving end of the test piece S, a torsional stress corresponding to the magnitude of the torque can be generated inside the test piece S. Then, by the load sensor 562 measures the magnitude of the torque applied to the test piece s.

Further, the support shaft 526 is rotatably supported in the middle by the fixed end side bearing 524. The fixed end side bearing 524 is also strongly fixed to the fixed end support plate 521 by means of bolting, welding, or the like. Next, a description will be given of a mechanism for fixing the fixed end support plate 521 to the lower frame 51A. As shown in Fig. 11, a pair of grooves 511 are formed in the lower frame 5j, and the fixed support plate 521 is fixed to the lower frame 51 by using the grooves 511 and the bolts 5, 12. On the support floor 521, there are seven (ie, 14) insertion holes 521a of the insertion bolts 512 along the respective grooves 511, and all the mounting bolts 512 of the through holes 521a are fixed to the lower frame. 51〇. The mouth and the cutting board are cut and strengthened. Next, the fixed end branch structure is fixed by the bolt 512. The twelfth figure is the eleventh figure: the plate 521 is as shown in the twelfth figure, and the groove 511 is a groove having a wide width of the width of the lower portion 5nb. In addition, 蝉2 邛 511a has a hexagonal hex wrench _&: 丨S19 & 检 形成 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 在 六角 六角 六角 六角 六角 六角 六角 511 511 511 511 C = The size of the female offender is only slightly smaller than the width of the lower portion 511b. The width of the screw is large, so that the upper portion 511a of the head nut 512 of the bolt 512, the end cutting plate 521 and the groove 511/the bud plate 521 are strongly fixed to the lower frame 510.疋端支30 200902971 Next, the configuration of the driving end support portion 530 will be described. As shown in the tenth figure, the drive end support portion 53A has an 537 for mounting the drive chuck for the test piece s = side chuck 574. A speed reduction mechanism 536 is provided on the surface of the mounting flange 537 opposite to the surface on which the drive 574 is mounted. Specifically, the tray is formed with a mounting flange on the output shaft of the speed reduction mechanism 536. The speed-changing mechanism 536 converts the high-speed, low-torque rotational motion of the input shaft to the low-speed, high-torque of the wheel-out shaft. Rotating motion. The output shaft is disposed (the drive that is transmitted to the test piece s via the flange 537 and the chuck 574) is fixed to the side frame 532 on the drive side of the drive end support portion 53. The side of the drive end side The frame 532 is strongly pressed by the welding end support member 531 of the end support portion 53G. The drive end support plate 531 is fixed to the lower frame 510 by the same fixing means as the fixed end support plate 521. The side frame 'M2 is a plate-shaped member that is substantially perpendicular to the rotation axis A, and a reinforcing rib 532a is formed at a corner portion formed by the side frame 532 and the driving end support plate 531. The rib 532a is also welded to The drive end support plate 531 and the i-quot; side end frame 532 on the drive end side. Therefore, the side frame 532 and the drive end plate 531 are integrated with rigidity back. As described above, the drive end support plate 1 is strongly fixed to the lower frame 510. Therefore, the side frame 532 is visible as a rigid body with the base B. The central portion (between the grooves 511 and 511) of the lower frame 51 is shaped like a hole portion 514. The hollow portion 514 is provided for making The drive end @ ^ ^ 53〇 slides on the lower frame 51 〇 The feed in the A direction has a 'dry machine. As shown in the tenth and eleventh figures, a feed screw 544 extending in a direction parallel to the rotation axis A is provided in the cavity portion 514. Feeding is only 544. Both ends are rotatably supported by a pair of bearings 54s, S46 (thirth figure) 31 200902971. Further, a nut 548 that engages with the feed screw 544 is fixed under the drive end support plate 531. When the driving end support plate 531 is not fixed to the lower frame 510 (that is, the state in which the bolt for fixing the driving end supporting plate 531 is loosened), the driving end supporting portion 530 can be made by rotating the feeding screw 544. Further, it is moved along the feed screw 544. Further, at one end of the feed screw 544 (on the side of the bearing 545), a handle 542 for rotating the feed screw 544 is provided. In this embodiment, the drive end support portion 530 is thus provided. The movement of the fixed end support portion 520 and the drive end support portion 53 is adjusted in accordance with the size of the test piece s. Further, a pulley 538a of the encoder 538 is attached to the lower portion of the mounting flange 537 of the side frame 532. The outer peripheral portion 537a of the mounting flange 537 is also The function of the pulley is set up on the pulley 538a of the encoder 538 and the pulley 537a of the mounting flange 537. The encoder 538 calculates the number of rotations of the mounting flange 537 by detecting the rotation angle of the pulley 538a. The rotation angle of the initial position of the edge 537 and the number of cycles during the repeated test can be displayed on the display portion 538b of the code 538. Therefore, the operator of the torque test machine 5〇1 can be displayed from the display portion of the encoder 538. The display content of 538b confirms the progress of the torque test and the like. Next, the arrangement of the input shaft 536a of the speed reduction mechanism 536 and the AC feeding motor 535 that applies torque to the input shaft will be described. The twelfth figure is a sectional view of the III-III of the eleventh figure. As shown in Fig. 13, the input shaft 536 of the deceleration mechanism 536 is coupled to the drive shaft 535a of the AC servo motor 535 via a rigid coupling 533. Therefore, a torsional stress can be applied to the test piece s by driving the Ac servo motor 535. Further, as shown in the figure, the AC servo motor 535 is fixed to the side frame 532 via the motor support frame 534. Further, the speed reduction mechanism 536 is embedded in the opening 532b formed in the side frame 532 to be firmly fixed. In the present embodiment, the speed reduction mechanism 536 is a wave gear reduction mechanism. The wave gear reduction mechanism has a knowledge that the input shaft and the wheel output shaft are coaxial. Therefore, in the present embodiment, the rotary shaft A and the drive shaft 535a of the gossip servo motor 535 are coaxial. Since the rotation axis A is coaxial with the drive shaft 535a of the AC servo motor 535, the torque test machine 501 has a shape that is substantially symmetrical with respect to the vertical plane including the rotation axis a. Therefore, the weight of the test machine 501 is good, and vibration is not easily generated during the test. Further, the wave gear reduction mechanism has a feature that the backlash is extremely small. Therefore, the accuracy of the fatigue test can be greatly improved by the 'fluctuating gear reducer' in the fatigue tester σ which applies the reverse load to the test piece. To the extent that the inventors are aware, there is no one in the prior fatigue testing machine that utilizes a wave gear reducer. The rigid coupling 533 of the present embodiment constitutes extremely high torque rigidity, and the drive shaft 53 torque applied to the AC servo motor 535 can be transmitted to the input shaft 536a of the speed reduction mechanism 536 with high reactivity. Hereinafter, the configuration of the coupler 533 will be described. Fig. 14 is a cross-sectional view showing the rigid coupling 533 and the ac feeding motor 535 coupled to each other via the rigid coupling 533, and the turning shaft of the moving shaft 535a and the speed reducing mechanism 536 is enlarged. j As shown in the figure, 'the rigid coupling 533 is in the shape of a hollow round bar (that is, a cylinder with a stepped thickness). The coupling 533 has a spare gear inserted into the reducer to enter the second generation 3 t... The input remaining portion (10) above the motor 535 is implemented. The diameter of the input shaft of the machine = 33 200902971 is smaller than the driving shaft of the AC feeding motor 535, so the outer diameter of the output side cylindrical portion 533a is larger than the round side. The outer diameter of the cylindrical portion 5 is small. Further, the output side cylindrical portion 533 & and the input side cylindrical portion 5 are moved inside (the right side of the output_tube portion gamma and the left side of the input side cylindrical portion 533b in the fourteenth drawing) are narrowed, respectively. The diameters of the tearing narrow portions 533e and the welcoming portions 533e and 5, respectively, and the driving shaft of the speed reducing mechanism 536 are substantially equal to the diameter of the driving vehicle of the AC motor 535. Therefore, the inner peripheral surface of the narrow portion 533e^ 533f and the input shaft 536a of the speed reduction mechanism 536 and the outer circumference of the drive shaft 53 of the AC servo motor 535 have no gaps, and the input shaft 536a of the deceleration mechanism 536 is The drive shaft 535 of the AC servo motor 535 is accommodated in the narrow portion 533e' 533f. The output side opening portion 533c and the input side opening portion respectively constitute the outer diameter of the input shaft 536a of the speed reduction mechanism 536 and the drive shaft 535a of the AC servo motor 535. Large diameter. The fixing rings 630 and 640 are used to fix the output side opening 533c and the input side opening 533d to the input shaft 536a of the speed reduction mechanism 536 and the drive shaft 535a of the AC servo motor 535, respectively. The fixing ring 630 has an inner wheel 632, an outer wheel 634, and a bolt 636. The outer circumferential surface 632a of the inner ring 632 has a tapered surface whose diameter is smaller toward the AC servo motor side (the right side in the drawing). Further, the inner circumference of the inner ring 632 = 632b becomes a cylindrical surface slightly larger than the outer diameter of the input shaft of the speed reduction mechanism 536. On the side of the speed reduction mechanism of the inner wheel 632 (left side in the drawing), the shape j is larger than the flange portion 032c on the outer side in the radial direction. A plurality of bolt holes 632d for inserting the bolts 636 into the direction of the rotation axis A are provided in the flange portion 632c. The inner circumferential surface 634a of the outer ring 634 becomes a tapered surface whose diameter is smaller toward the side of the AC servo horse 34 200902971. Further, the outer circumferential surface 634b of the outer ring 634 is a cylindrical surface slightly smaller than the diameter of the output side opening portion 533c. Further, a plurality of female threads 634c that engage with the bolts 630 are formed in the outer wheel 634. The outer wheel 634 and the inner wheel 632 are inserted into the gap between the output side opening 533c and the input shaft 536a of the speed reduction mechanism 536, and then the inner wheel 632 is fixed to the outer wheel 634 by the bolt 636, further by the fastening bolt illusion 6, and the inner wheel 632 The inner peripheral surface 632b strongly presses the input shaft 536a of the speed reduction mechanism 536, and the cylindrical surface 63 of the outer wheel 634 strongly presses the output side opening = 533c. As a result, by the static friction generated, the speed reduction mechanism 536 is fixed to the output side cylinder of the rigid coupling 533, and is formed into a body. In addition, the figure shows that each of the two displays the two-hole phantom and the female thread 634c'. However, in fact, the speed-reducing mechanism 5 3 6 is the fourth you A cb, (for example, Η) group. A plurality of the same, the fixing ring 64 and the bolt 646 are provided on the circumference of the center. The outer wheel 642 is outside/face. The inner wheel 642 and the outer wheel 644 have tapered surfaces on the mechanism side. This 2a is a cylindrical surface whose diameter is reduced toward the inner circumferential surface of the second wheel (4) of the AC servo motor 535. Below the inner wheel 642, the flange 642c on the side of the outer diameter of the mountain 535a is slightly larger. The flange portion 4 is formed with a plurality of screws 42C which are enlarged in the radial direction and inserted in the direction of the rotation axis A. The plurality of bolts 646 644a are formed to have a diameter toward the reduction 撼 642d. The inner peripheral surface of the outer ring 644 has a tapered surface which becomes smaller on the outer peripheral side of the outer ring 644. In addition, the cylindrical surface is slightly smaller in diameter. Further, a female screw 644c is formed in a plurality of fish snails 644 at a position corresponding to the straight portion of the wheel-in opening portion 533d, and the outer ring 644 and the inner wheel 642 are inserted into the bolt hole 642d, and the female screw 644c is engaged. The clearance between the drive shaft 535 & the rain inlet side opening 533d and the AC servo a of the motor 535 is secondarily fixed to the outer wheel 644 by bolts 646 35 200902971 = further by the fastening bolt 646 and the cylindrical surface of the inner wheel 642 642b strongly oppressed people (: servant

^, 535a, outer peripheral surface 644 outer peripheral surface (10) pressure = opening portion 533d. By the static friction that occurs, Xiaoguo is fixedly fixed to the rigid side of the rigid coupling 533 from the driving shaft, and the two form a body. In addition, the drawings are different, and the bolts 646, the bolt holes 64 and the female threads 64 讣, however, on the circumference centering on the central axis of rotation of the drive shaft of the AC feeding motor 535 There are a large number (for example, a group of 1).

. Since the thickness of the output side cylindrical portion 533 & and the input side rounded portion 533b of the rigid coupling 533 is sufficiently large, the rigid coupling can be substantially regarded as a rigid body. Therefore, the rigid coupling 533 can transmit the torque ' acting on the drive shaft 535a of the AC servo motor 535 to the speed reduction mechanism 536 with high reactivity. Next, the configuration of the control measuring unit of the torque testing machine 5〇1 of the present embodiment will be described. The fifteenth diagram is a block diagram of the control measuring unit 700 of the torque testing machine 501 of the present embodiment. The torque testing machine 501 of the present embodiment can perform the fatigue test in a short time, and can apply a reverse torque load on the test piece in a short cycle (a few tens of cycles per second). The control measurement unit 700 of the torque test machine 501 has a set value instruction unit 710, a drive control unit 720, and a measurement unit 750. The set value indicating unit 710 is a unit for indicating how to apply a torsional stress on the test piece Si. Specifically, the set value instructing unit 710 outputs the angle of the mounting flange 537 (or the output shaft of the speed reducing mechanism 536) to the initial position as a signal, and outputs it to the unit of the drive control unit 720. The set value indicating unit 710 has an input interface 712 and a waveform generating circuit 714. 36 200902971 Input interface 712 is used to connect the interface of the two display: workstation. Torque test machine Π. ;: = Workstation' indicates how to displace the lower stage 531. For example, if the operator is operating the workstation, the torque angle of each unit is rotated and sent to the input interface 712. Guard: The fatigue test of the repeated load on the sheet S = station, and the amplitude, frequency and waveform of the input torque angle, or the waveform of the triangle wave, etc., and the sine wave, 迗汛 to the input interface 712. Enter in 铨

The indication of facet 712 is passed to waveform generation circuit 714. The 'J waveform generation circuit 714 interprets the change from the input interface 71 to the angle of the mounting flange 537 from the initial position, which will be the same as the drive control unit 72. In addition, the fatigue test 4 is not limited to twisting the test piece s with a single sine' rate, and the test piece can be twisted from a function having a combination of various amplitudes and frequencies according to the == one waveform and the frequency machine. . The mounting flange 537 can also be driven as a function of time, depending on the multiplication by the frequency: 绫2 Ϊ function.

Politics 71 = The angle of 537 is used as a digital signal to generate electricity from the waveform =: 14 output. Therefore, the "tiger" from the waveform generating circuit m to the drive control 720 is first input to the D/A converter 722 to be converted into a signal. The angle information of the mounting flange claws converted into analog signals is transmitted to the amplifier 724. Then, the amplifier 724 amplifies the mounting flange 537 # angle information transmitted from the D/A 722, and outputs it. - As described above, in the present embodiment, various tests are performed by driving the opening flange 537 by the AC servo motor 535. Here, the AC servo motor 535 has a code 37 200902971 for detecting the number of revolutions of the drive shaft 535 & (the tenth figure), and the encoder detects the number of revolutions sent to the current position operation circuit 726 of the drive control unit 720. . The position calculating circuit 726 now outputs the current angle of the mounting flange 537 based on the detection result of the encoder of the AC servo motor 535. Then, the difference between the output of the amplifier 724 and the output of the current position calculating circuit 726 (i.e., the signal corresponding to the difference between the target angle of the mounting flange 537 and the current angle) is sent to the current generating circuit 728. The current generating circuit 728 generates a three-phase current output to the AC servo motor 535 based on the received signal and outputs it to the AC servo motor 535. As a result, the AC servo motor 535 is driven to bring the angle of the mounting flange 537 to the target angle. The torque applied to the test piece S by driving the mounting flange 537 is detected by the load cell 562 and the bridge circuit 756 for taking out the amount of deformation of the load cell 562 as an electrical signal. The magnitude of the detected torque is converted to a digital signal by A/D converter 758 and sent to the workstation via output interface 759. The workstation counts the magnitude of the torque transmitted from the output interface 759, and produces a pattern in which the time axis is the horizontal axis and the torsional stress applied to the test piece is plotted on the vertical axis. Further, a so-called feedback control for transmitting the torque of the output of the A/D converter 758 to the waveform generating circuit 714 and changing the torque of the test piece S in response to the torque may be performed. If the rotation angle of the mounting flange 537 is not proportional to the torque, that is, when the test piece S is lifted and lowered, the amplitude of the torsion angle can be controlled. By using the above-described torque testing machine 501, it is possible to perform static breaking test, fatigue test, and the like of the test piece. Here, in the present embodiment, the AC servo motor 535 having high reactivity and high torque is used to twist the 38 200902971 test piece S. Therefore, the torque of the torque testing machine 5 〇 1 and kN· m is applied to the test piece s, and η dares to reach a high frequency of several hundreds to apply a reverse load to the test piece s. Therefore, it is possible to use dozens of torque test machines 5 of the example (U can break the work in a short time, and can shorten the test time.) The test piece is fatigued, and when the configuration of the embodiment is used, The Ac servo diagram for the power source for twisting the test piece S is used to rotate the drive shaft 535 of the AC servo motor 535 to 535, and the side frame fixed to the same plate surface as the speed mechanism 536 is tweeted. By subtracting the drive shaft of the AC servo motor 535, the relative position of the input shaft 536a is accurately set to 1, and the transmission of the structure 536 easily and more accurately performs the H of the AC servo motor 535. Thus, the speed can be reduced. The centering of the input shaft 536a of the mechanism 536. The relative position of the shaft 535a and the forming plate surface needs to be highly accurate by f-: the high-precision and stable maintaining of each position; the piece == In the configuration of the embodiment, the centering of the AC feeding motor 535 (the driving shaft 2 and the input shaft 536a of the speed reducing mechanism 536 can be performed with high precision. Therefore, the driving of the AC servo motor 535 is caused by the difference. The bending stress between the 5& and the input shaft 536a of the subtractive structure 536 is small. A coupler generally used for coupling an input shaft of a motor and a speed reduction mechanism is a soft coupler constructed by interposing a material having low rigidity (rubber or the like) to relieve bending stress. However, in this embodiment As described above, since the centering of the two shafts can be performed with high precision, the rigid coupling 533 formed of a material having high rigidity can be used. Therefore, the driving shaft 535a acting on the AC servo motor 535 can be made highly reactive. The torque is transmitted to the input shaft 536a of the speed reduction mechanism 39 200902971 536. In the present embodiment, the drive shaft 535 & of the AC servo motor 535 and the input shaft 536 of the speed reduction mechanism 536 are coupled by the rigid coupling 533. The invention is not limited to the above-described constituents, that is, 'can also be replaced by Π!, and the semi-coupling coupler of the second embodiment of the present invention is coupled to the drive shaft 53Sa of the Ac servo motor 535 and the wheel of the speed reduction mechanism 536. The first shaft and the second embodiment of the present invention fix the servo motor, the linear guide rail and the bearing on the early support plate (the work table 33). These components are combined with the support plate as a reference. Therefore, the accuracy of the component is easy. In addition, since the servo motor, the wire can be held, and the phase is smaller, the thermal expansion can be misused. In addition, since the number of connection points from the ball screw to the servo horse = drive shaft is kept to a minimum, once the centering of the drive shaft of the feed screw and the servo motor is performed, the temple is made. It is easy to accurately match the center of rotation of the drive shaft of the motor with the center of rotation of the feed screw (the difference is within several tens of μm). Because of the non-linearity of the feed screw and the motor (4) The bending stress occurring on the rotating portion is suppressed by the coupling, the heart, and the coupling angle. Therefore, the rigid coupling 11 or the semi-rigid coupling screw and the motor drive shaft can be highly reactive. ^ Turn to drive. Thus, with the configuration + of the embodiment of the present invention, the feed screw mechanism can be used to drive the crosshead, and the load (strain) is applied to the general test machine of the job at a high cycle. In addition, such a linear actuator drives a linear actuator even in the state of a fixed body such as a crosshead, and excitation is also useful for the test body excitation tester. In addition, the coupling portion of the coupler preferably has a torque of 200902971 equal to or greater than the drive shaft of the feed screw and the servo motor. In addition, the rigid coupling has a rigid cylindrical body equal to or above the rotation axis of the feed screw and the servo motor, and is inserted into the feed screw from one end thereof, and the drive shaft of the servo motor is inserted into the cylinder from the other end. The body is fixed. In the cylindrical body, one of the inner holes into which the feed screw and the drive shaft of the servo motor are inserted is preferably a narrow portion that is accommodated substantially without a gap with the circumferential surface of the feed screw and the drive shaft of the servo motor. Further, it is preferable to fix the feed shaft of the feed screw and the motor and the rigid coupling by inserting a fixing ring between the inner circumferential surface of the cylindrical body of the rigid coupling and the circumferential surface of the feed screw and the drive shaft of the motor. For example, the fixing ring has: an inner wheel whose outer circumference is a tapered surface; an inner circumference which is a tapered outer surface corresponding to the outer circumference of the inner wheel; and a state in which the outer circumference of the outer wheel abuts the inner circumference of the outer wheel, and any one of the inner wheel and the outer wheel The other side of the direction is pressed against the extrusion device in its axial direction. According to this configuration, the drive shaft of the motor and the feed screw can be more strongly coupled, and the torque of the drive shaft of the motor can be transmitted to the feed screw with higher reactivity. The universal test machine and the linear actuator of the first and second embodiments of the present invention can also use a semi-rigid coupling instead of the rigid coupling. By feeding the drive shaft and the feed screw of the motor with a semi-rigid coupling that has flexibility in the bending direction and hinders vibration in the direction of extension of the drive shaft of the motor, the feed screw can be driven with high reactivity, even if There are a number of axis deviations that still do not cause extreme large internal soft curvatures, but can be driven smoothly and can block vibrations in the direction of the motor drive shaft. The semi-rigid coupling should preferably have a viscoelastic element formed of resin or rubber. Further, the semi-rigid coupling constitutes the vibration damping rate of the drive shaft of the servo motor to maximize the natural vibration number of the drive shaft. With this configuration 41 200902971 into the 'semi-rigid coupling π through the drive shaft to transmit the * elastic element can effectively attenuate the vibration from the horse to the vibration of the horse or the axis of the shaft, so that 'Semi-rigid joint & 'two outer wheel; and an inner wheel provided with one elastic element belonging to a rigid body element. Between the 7's respectively, the elastic element is included or the center of the inner wheel is reported, and the tapered hole is formed in the center of the outer wheel and perforated. In addition, in the (4) of the use of the evening, the axis of the joint of the cylindrical column

;;:rr one inner circumference = the end of the perforation inserted into the feed screw and the servo motor's drive shaft 抵-shaped surface abutment - the outer wheel cone (four) * (four) cone, it Λ straw by the bolts to each other The wheel is coupled to its shaft via the inner wheel. By doing so, it is extremely simple to construct a semi-rigid coupling that transmits with high reactivity. Thereby, a vibrational three-hole > and a reactive south linear actuator are realized. Further, the opening portion of the feed screw is formed on the support plate, and the outer wheel of the bearing rotatably supporting the feed screw is fixed in the opening portion. According to this configuration, since the bearing, the linear guide, and the servo motor are integrally formed, it is possible to maintain a state in which the center of rotation of the drive shaft of the motor and the center of rotation of the feed screw are more accurately matched. In this case, when the bearing is combined with the combined angular ball bearing, the bearing can be applied to the large load in the thrust direction of the feed screw and the feed screw can be rotatably supported. Further, it may be configured such that the screw-type ball screw is fed and the nut is a nut for the ball screw, that is, the crosshead is driven by the ball screw mechanism. When constructed in this way, the crosshead can be moved back and forth at high speed with a small backlash, and the speed of the load can be made higher. 42 200902971 Two = structure = moving block with fixed guide and movable part of linear guide, moving block has: concave part surrounding the obstruction; ^ moving direction of moving block and groove formed in the groove of the concave part forms closed circuit Both ends of the moving direction of the ground and the groove

When the path is looped in the path and is located in the ditch, it is mixed with the front: the obstruction. Furthermore, four closed circuits are formed in the moving block, and the balls disposed in the respective grooves of the two closed paths have a contact angle of ±45 degrees to the radial direction of the linear guide, and the other two The balls disposed in each of the closed channels have a contact angle of ±45 degrees to the reverse radial direction of the linear guide. When the linear guide thus constructed is used, even if a large load is applied to the test piece, the nut of the feed screw mechanism does not wobble and smoothly moves along the linear guide. In the torque testing machine of the third embodiment of the present invention, the squatting motor and the slamming mechanism are fixed to the first supporting member (the side frame 532 on the driving end side) fixed to the frame. = In the constitution of the present invention, both the fixed ship motor and the speed reduction mechanism are attached to the first support member of the single member. These members are centered on the first branch member. Thus, it is ensured that the accuracy of each component is easy. In addition, since the distance between the servo motor and the speed reduction mechanism can be made small, the error caused by the thermal expansion can be minimized. In addition, since the amount of connection from the drive shaft of the feeding motor to the input shaft of the speed reduction mechanism is minimized, once the servo motor is accurately drilled and the input shaft of the deceleration mechanism is fixed, the maintenance is maintained. It is easy to make the rotation of the drive shaft of the motor coincide with the rotation of the feed screw accurately (within an error of several tens of μηι). Therefore, 43 200902971 can be connected to the eight-axis and the motor by the speed reduction mechanism ( Eccentricity and coupling angle) The non-linearity of the screw is small. Because it can have high torsion rigidity, the bending stress is extremely coupled to the deceleration mechanism, and the semi-rigid, the rotation of the wheel of the 吏 reduction mechanism: the moving shaft can be high The cycle will twist the test mechanism with the torque mechanism, and the input shaft of the drive and the speed reduction mechanism and the above-mentioned feeding force test unit of the f-force test machine should have a coupling axis with the deflation mechanism. Torque rigidity equal to or above. In addition to the servo motor, the step is to be fixed to the frame (the side frame 522 on the fixed end side), the second support member, "the beam is supported by the arm : 'The fixing portion is fixed to the frame. In this configuration, the fixed member-side bearing device for measuring the shaft portion of the shaft portion and the second holding portion is fixed between the two members. Reading the ground support second, in addition, the speed reduction mechanism should be the wave gear reduction ball structure and the planetary # turbine-like other depreciation structure @ #. The turbine speed reduction mechanism repeatedly twists the test piece when the tooth = because = wheel 5 = two labor ^ 1 The gear reducer member is fixed, and the south is rigid and integrated with the first-cut member. [Schematic description] The first view of the first embodiment of the present invention is the first test machine of the present invention. 2 is a longitudinal cross-sectional view of the movable portion of the universal residual test machine of the first embodiment of the present invention and its surroundings. The third working view of the first embodiment of the present invention is a universal test coupling of the first embodiment of the present invention. The fourth drawing is a longitudinal sectional view of the vicinity of the through hole of the universal testing machine of the first embodiment of the present invention. σ , the fifth drawing is the universal testing machine 2 of the first embodiment of the present invention. Cut off the plane in the direction perpendicular to the long axis of the road . FIG sectional block <

The sixth figure is the I-! section view of the fifth figure. The seventh drawing is a block diagram of the measuring unit of the universal testing machine of the first embodiment of the present invention. Second and eighth figures show an example in which the linear actuator of the first embodiment of the present invention is applied to an excitation test machine. The ninth drawing is a longitudinal sectional view of a semi-rigid coupling of a universal testing machine according to a second embodiment of the present invention. The tenth drawing is a view of a torque testing machine of a third embodiment of the present invention. The eleventh drawing is a plan view of a torque testing machine of a third embodiment of the present invention. Figure 12 is a cross-sectional view of the II-II of the eleventh figure. The thirteenth picture is a sectional view of the III-III of the eleventh figure. Fig. 14 is a longitudinal sectional view showing the rigid coupling of the torque testing machine of the third embodiment of the present invention and its surroundings. Fig. 15 is a block diagram showing a control measuring unit of the torque testing machine of the third embodiment of the present invention. [Main component symbol description] 45 200902971 1 Universal test machine 10 Machine frame part 10, machine frame part 11 Foot part 11a Upper surface lib Inner side surface 12 Guide rod 13 Top portion 13a Through hole 20 Fixing portion 21 Upper stage 21a Through hole 21b Bolt hole 21c Bolt 22 Feed screw 23a Nut 24a Radial ball bearing 24b Bearing support 25 Motor 25a Drive shaft 26 Gear box 26a Output shaft 26b Drive pulley 27 Endless belt 28 Attachment 30 Movable part 31 Lower stage 31a Ball wire Bar nut 31b Crosshead 33 Table 33a Side 33b Lower 33c Upper 33d Through hole 33e Female thread 34 Rigid coupling 34a Upper cylindrical portion 34b Lower cylindrical portion 34B Cylindrical body 34c Upper opening 34d Lower opening 34e Narrow portion 34f narrow portion 35 AC servo motor 35a drive shaft 36 ball screw 36a screw portion 36b shaft portion 36c male thread 37 motor support frame 40 linear guide 42 guide frame 42a side wall 42b upper wall surface 46 200902971 42c opening portion 144 outer wheel 44 inner rail 144a Circumference 44a groove 144b Cylindrical surface 44a, groove 144c female thread 46 moving block 146 bolt 46a groove 150 bearing portion 46a, groove 151 combined angular ball bearing 46b ball 151a angular ball bearing 46c exit path 151b angular ball bearing 46d U-shaped path 152 first bearing mounting member 130 Fixing ring 152a Flange portion 132 Inner wheel 152b Through hole 132a Outer peripheral surface 153 Second bearing mounting member 132b Inner peripheral surface 153a Through hole 132c Flange portion 153b Blind plate 132d Bolt hole 154 First ring 134 Outer wheel 155 Second ring 134a inner peripheral surface 156 nut 134b outer peripheral surface 157a oil seal 134c female thread 157b oil seal 136 bolt 158a bolt 140 fixing ring 158b bolt 142 inner wheel 159 lining 142a outer peripheral surface 200 control measuring portion 142b inner peripheral surface 210 set value indicating unit 142c convex Edge 212 Input Interface 142d Bolt Hole 214 Waveform Generation Circuit 47 200902971 220 Drive Control Unit 511b Lower 222 D/A Converter 512 Bolt 224 Amplifier 512a Hexagon L 226 Current Position Operation Circuit 513 Nut 228 Current Generation Circuit 514 Cavity 254 Load Sensor 520 fixed end Bracing portion 256 Bridge circuit 521 Fixed end support plate 258 A/D converter 521a Through hole 259 Output interface 522 Fixed end side side frame 300 Semi-rigid coupling 522a Reinforcement rib 320 Outer wheel 524 Fixed end side bearing 340 Outer wheel 526 Support Shaft 322 Inner side 527 Mounting flange 342 Inner side 530 Drive end support 360 Inner wheel 531 Drive end support plate 360a Flange portion 532 Drive side side frame 362a Round hole 532a Reinforcement rib 362b Round hole 532b Opening 364 Outer side 533 Rigid coupling 366 Outer side 533a Output side cylindrical portion 324 Bolt hole 533b Input side cylindrical portion 368 Bolt hole 533c Output side opening portion 382 Bolt 533d Input side opening portion 501 Torque test machine 533e Narrow portion 510 Lower frame 533f Narrow 511 a pair of grooves 535 AC servo motor 511a upper 535a drive shaft 48 200902971 536 speed reduction mechanism 640 fixing ring 536a input shaft 642 inner wheel 537 mounting flange 642a outer peripheral surface 537a outer peripheral portion 642b inner peripheral surface 538 encoder 642c flange portion 538a Pulley 642d bolt hole 538b display part 644 outer wheel 539 Endless belt 644a Inner circumferential surface 544 Feed screw 644b Outer circumferential surface 545 Bearing 644c Female thread 546 Bearing 646 Bolt 548 Nut 700 Control measuring unit 562 Load sensor 710 Setting value is not early 572 Chuck 712 Input interface 574 Chuck 714 Waveform Generation circuit 572a Claw 720 Drive control unit 574a Claw 722 D/A converter 630 Fixing ring 724 Amplifier 632 Inner wheel 726 Current position operation circuit 632a Outer peripheral surface 728 Current generation circuit 632b Inner peripheral surface 750 Measurement unit 632c Flange portion 756 Bridge circuit 634 outer wheel 758 A/D converter 634a inner circumferential surface 759 output interface 634b outer circumferential surface B pedestal 634c female thread C car 636 bolt s test piece 49

Claims (1)

200902971 X. Patent application scope: 1. A universal testing machine having: a servo motor that rotates the drive shaft back and forth; a feed screw; a coupling that couples the feed screw to the drive shaft of the servo motor a nut that engages with the feed screw; a linear guide that limits the direction of movement of the nut to only the axial direction of the feed screw; and a fixed portion that abuts or fixes one end of the test piece; The head is abutting or fixing the other end of the test piece, fixed to the nut and moving together with the nut; and a support plate to which the servo motor and the linear guide are fixed. 2. The universal testing machine of claim 1, wherein the coupling portion of the coupling has a torsional rigidity equal to or greater than a driving axis of the feed screw and the servo motor. 3. A universal test machine as claimed in claim 2, wherein the aforementioned coupling is a rigid coupling. 4. The universal testing machine of claim 3, wherein the rigid coupling has a cylindrical body having a torsional rigidity equal to or greater than a driving axis of the feed screw and the servo motor, and respectively One end of the feed screw is inserted into the feed screw, and the drive shaft of the servo motor is inserted from the other end to be fixed to the cylindrical body. 5. The universal testing machine of claim 4, wherein a part of the inner hole of the feed screw and the drive shaft of the servo motor is inserted into the cylindrical body to be the same as the feed screw and the servo 50 200902971 The narrow surface of the peripheral surface of the drive shaft of the motor is roughly received without gaps. 6. The universal test machine of claim 4, wherein the inner peripheral surface of the inner hole of the cylindrical body is fitted and fixed between the feed screw and the circumferential surface of the drive shaft of the servo motor a ring, and the feed screw and the drive shaft of the servo motor are fixed to the rigid coupling. 7. The universal testing machine of claim 6, wherein the fixing ring has; the inner wheel has a tapered surface; the outer wheel has an inner circumference which becomes a tapered surface corresponding to the outer circumference of the inner wheel; and The pressing device presses one of the inner and outer wheels in the axial direction in a state in which the outer circumference of the inner ring abuts against the inner circumference of the outer ring. 8. The universal test machine of claim 2, wherein the coupler constitutes a semi-rigid coupler having flexibility in a bending direction and obstructing vibration in a direction in which the drive shaft of the servo motor is extended. 9. The universal testing machine of claim 8 wherein said semi-rigid coupling comprises a viscoelastic element. 10. The universal testing machine of claim 9, wherein at least a portion of the aforementioned viscoelastic member is formed of a resin. 11. The universal testing machine of claim 9, wherein at least a portion of the aforementioned viscoelastic member is formed of rubber. 12. The universal test machine of claim 8, wherein the semi-rigid coupling constitutes a vibration damping rate in a direction of a drive shaft of the servo motor, and is maximum in a natural vibration number of the drive shaft. 51 200902971 13. The universal testing machine of claim 8 wherein said semi-rigid coupling has: an outer wheel that is a rigid body member that is formed with a tapered hole in the center; and an elastic element or viscoelasticity The inner wheel of the component is disposed between the outer wheel and the cylindrical through hole formed by the shaft coupled to the center, and is formed at each end of the outer circumferential direction to be tapered with the outer wheel Inserting a tapered surface of the inner circumference of the hole; inserting the feed screw and the drive shaft of the servo motor into the through hole of the inner wheel such that the tapered surface of the inner wheel abuts the tapered hole of the outer wheel In the circumferential direction, the shaft is coupled via the inner wheel by fixing the aforementioned outer wheel to each other with bolts. 14. The universal testing machine of claim 1, wherein the support plate is provided with an opening through which the feed screw is inserted, and the opening is fixed with a bearing rotatably supporting the feed screw. The outer wheel, the aforementioned bearing has an angular ball bearing. 15. The universal test machine of claim 14, wherein the aforementioned bearing has a combination face type ball bearing of a face combination type in which the front faces of the pair of angular ball bearings are opposed to each other. 16. The universal testing machine of claim 1, wherein the feed screw is a ball screw, and the nut is a nut for a ball screw. 17. The universal test machine of claim 1, wherein the support plate is a metal plate or a plurality of metal plates are integrated by welding. 18. The universal test machine of claim 1, wherein the support plate is welded to the foot of the universal test machine. 19. The universal testing machine of claim 1, wherein the wire 52 200902971 rail has: a first portion fixed to the fixing portion, and a second portion fixed to the nut, the first portion and the first portion One of the two parts has a track, and the other side is engaged with the track, and has a moving block movable along the track, the moving block has: a recess that surrounds the track; a groove that is in the recess Forming along the moving direction of the moving block; the exiting path is formed inside the moving block, and the groove is formed in a closed circuit to connect the two ends of the groove in the moving direction; and the plurality of balls are in the foregoing It circulates in a closed circuit and abuts the aforementioned track when it is located in the groove. 20. The universal testing machine of claim 19, wherein four of the aforementioned closed circuits are formed in the moving block, and wherein the two closed circuits are disposed in the respective grooves and have a diameter on the linear guide. The direction of the contact is generally a contact angle of ±45 degrees, and the balls of the other two closed paths disposed in the respective grooves have a contact angle of ±45 degrees to the reverse radial direction of the linear guide. 21. The universal testing machine of claim 1, further comprising at least one guide shaft for fixing the leg portion, wherein the fixing portion is fixed to the fixing portion by a guide shaft In the guide shaft for the fixing portion, the fixing portion is movable along the guide shaft for the fixing portion in a state where the fixing portion is not sandwiched by the fixing portion. 22. The universal testing machine of claim 21, further comprising a fixing portion driving device for causing the fixing portion to be along a state in which the fixing portion does not sandwich the guiding portion for the fixing portion The fixed portion is moved by a guide shaft. 53 200902971 23. The universal test machine of claim 22, wherein the fixed portion driving device moves the fixed portion by a feed screw mechanism. 24. A linear actuator having: a servo motor; a feed screw; a coupler coupling the feed screw to a drive shaft of the servo motor; a nut engaged with the feed screw; a linear guide, The movement direction of the nut is limited only to the axial direction of the feed screw; and the support plate is fixed with the servo motor and the linear guide. 25. The linear actuator of claim 24, wherein the coupling portion of the coupler has a torsional rigidity equal to or greater than a drive shaft of the feed screw and the servo motor. 26. The linear actuator of claim 25, wherein the coupler is a rigid coupler. 27. The linear actuator of claim 26, wherein the rigid coupling has a cylindrical body having a torsional rigidity equal to or greater than a drive shaft of the feed screw and the servo motor, and one end thereof respectively The feed screw is inserted, and the drive shaft of the servo motor is inserted from the other end to be fixed to the cylindrical body. 28. The linear actuator of claim 27, wherein a portion of the inner hole of the feed screw and the drive shaft of the servo motor is inserted into the cylindrical body to be driven by the feed screw and the servo motor. A narrow portion of the circumferential surface of the shaft that is accommodated substantially without a gap. The linear actuator according to claim 27, wherein the inner peripheral surface of the inner hole of the cylindrical body is fitted and fixed between the feed screw and the circumferential surface of the drive shaft of the servo motor. a ring, and the feed screw and the drive shaft of the servo motor are fixed to the rigid coupling. 30. The linear actuator of claim 27, wherein the fixing ring has: an inner wheel whose outer circumference is a tapered surface; an outer wheel whose inner circumference is a tapered surface corresponding to an outer circumference of the inner wheel; and a pressure spreading device In a state in which the outer circumference of the inner ring abuts against the inner circumference of the outer ring, one of the inner wheel and the outer wheel is pressed in the axial direction. 31. The linear actuator of claim 25, wherein the coupler constitutes a semi-rigid coupler having flexibility in a bending direction and obstructing vibration in a direction in which the drive shaft of the motor is extended. 32. The linear actuator of claim 31, wherein the semi-rigid coupling comprises a viscoelastic element. 33. The linear actuator of claim 32, wherein at least a portion of the aforementioned viscoelastic member is formed of a resin. 34. The linear actuator of claim 32, wherein at least a portion of the aforementioned viscoelastic member is formed of rubber. 35. The linear actuator of claim 31, wherein the semi-rigid coupling constitutes a vibration damping rate in a direction of a drive axis of the motor, and is maximum in a natural vibration number of the drive shaft. 36. The linear actuator of claim 31, wherein the semi-rigid coupling has: 55 200902971 an outer wheel that is a rigid body member that is formed with a tapered hole at a center; and an elastic member or a viscoelastic member The inner wheel is disposed between the outer wheel and defines a cylindrical through hole for connecting to the shaft of the center, and inner circumferences of the tapered hole respectively formed by the outer wheel are formed at both ends of the outer circumference Engaging the tapered portion; inserting the feed screw and the drive shaft of the servo motor into the through hole of the inner wheel such that the tapered surface of the inner wheel abuts against the inner circumference of the tapered hole of the outer wheel The aforementioned outer wheel is fixed to each other by bolts, and the shaft is coupled via the inner wheel. 37. The linear actuator of claim 24, wherein the support plate is provided with an opening through which the feed screw is inserted, and an outer wheel rotatably supporting a bearing of the feed screw is fixed in the opening. The aforementioned bearings have angular ball bearings. 38. The linear actuator of claim 37, wherein the aforementioned bearing has a combined front type combined angular ball bearing that combines the front faces of the pair of angular ball bearings. 39. The linear actuator of claim 24, wherein the feed screw is a ball screw, and the nut is a nut for a ball screw. 40. The linear actuator of claim 24, wherein the support plate is a metal plate or a plurality of metal plates are integrated by welding. The linear actuator of claim 24, wherein the linear guide has: a first portion fixed to the fixing portion, and a second portion fixed to the nut, one of the first portion and the second portion The other side is engaged with the aforementioned track and has a moving block movable along the track. The moving block has: 56 200902971 a recess that surrounds the track; a groove that is in the recess, Forming along the moving direction of the moving block; the exiting path is formed inside the moving block, and the groove is formed in a closed circuit to connect the two ends of the groove in the moving direction; and the plurality of balls are in the closed circuit It circulates and abuts the aforementioned way when it is located in the groove. 42. The linear actuator of claim 41, wherein four of the aforementioned closed circuits are formed in the moving block, and two of the four closed circuits are disposed in a radial direction of the linear guide. The direction is roughly a contact angle of 45 degrees, and the other two closed paths of the balls disposed in the respective grooves have a contact angle of ±45 degrees to the reverse radial direction of the linear guide. 43. A torque testing machine having: a frame fixed to a base of the machine; a servo motor; a speed reducing mechanism; and a coupling coupling the input shaft of the speed reducing mechanism and the driving shaft of the servo motor a first gripping portion fixed to an output shaft of the speed reducing mechanism and holding one end of the test piece; a second gripping portion fixed to the frame and holding the other end of the test piece; and the first A support member fixed to the frame and fixed to the servo motor and the speed reduction mechanism. 44. The torque testing machine of claim 43, wherein the coupling portion of the coupling has a torque rigidity equal to or greater than an input shaft of the speed reduction mechanism and a drive shaft of the servo motor. 45. The torque testing machine of claim 40, wherein the coupling is a rigid coupling. 46. The torque testing machine of claim 44, wherein the coupling constitutes a semi-rigid coupling that is flexible in a bending direction and that hinders vibration in an extending direction of a drive shaft of the motor. 47. The torque testing machine of claim 43, further comprising a second supporting member fixed to the frame; the second holding portion having a shaft portion; wherein the shaft portion is cantilevered The second support member is fixedly supported to the second support member, and the second grip portion is fixed to the frame. 48. The torque testing machine of claim 47, further comprising a fixed end side bearing device fixed to the frame and rotatably supporting the shaft portion of the second holding portion. 49. The torque testing machine of claim 43, wherein a load sensor for measuring a torque applied to the test piece is fixed between the shaft portion and the second support member. 50. The torque testing machine of claim 43, wherein the speed reducing mechanism is a wave gear reduction mechanism. 51. The torque testing machine of claim 45, wherein the wave gear reduction mechanism is fixed by embedding the first support member. 58