JP2010266266A - Testing machine equipped with linear reciprocating mechanism - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a testing machine for applying a linear reciprocating motion to an object to be tested. <P>SOLUTION: A linear reciprocating mechanism 100 of the testing machine 300 includes: an internal sun gear 102 fixed on a crank member 104; a planet gear member 103 rotating and revolving while engaging a planet gear 131 with the internal sun gear 102, the planet gear having a pitch circle diameter that is 1/2 of the pitch circle diameter of the internal sun gear 102; the crank member 104 disposed in a crank case 101 so as to rotate coaxially with the center line of the internal sun gear 102, and rotatably and revolvably supporting the planet gear element 103; and an action part 147 disposed on the planet gear member 103 on the pitch circle of the planet gear 131 when viewed from the infinity point in the rotating axis direction of the planet gear 131, and perform the linear reciprocating motion in association with the rotation of the crank member 104. <P>COPYRIGHT: (C)2011,JPO&INPIT

Description

  The present invention relates to a testing machine provided with a linear reciprocating mechanism that causes a linear reciprocating motion to act on a device under test, for example, a friction testing machine and a fatigue testing machine.

  For example, as disclosed in Japanese Patent No. 2850054 (Patent Document 1) and Japanese Patent Application Laid-Open No. 2007-177760 (Patent Document 2), the friction test is performed by sliding a test object against a flat plate while sliding it. Tests for measuring resistance have been proposed. In the fatigue test, for example, as described in Japanese Patent Application Laid-Open No. 2006-189288 (Patent Document 3), a linear reciprocating mechanism is used in a mechanism that repeatedly applies a tensile or bending load to a test object. There is.

  In such a case, a mechanism combining a ball screw or a hydraulic cylinder and a servo valve is used as a mechanism for causing a linear reciprocating motion to act on the DUT. According to such a mechanism, the DUT can be linearly reciprocated more accurately.

  In addition, as disclosed in, for example, Japanese Patent Application Laid-Open No. 2007-2332026 (Patent Document 4), there is a testing machine that measures a force acting on a cylinder when a piston slides in the cylinder. In this publication, a piston is slidably accommodated in a cylinder and connected to a crankshaft via a connecting rod. The piston linearly reciprocates while being guided by the cylinder as the crankshaft rotates.

  Further, although there is no disclosure regarding the use of a friction tester or a fatigue tester, LWJ Co., Ltd. has developed a linear reciprocating mechanism that obtains a linear reciprocating motion from the rotational motion of the crankshaft. There is a proposal of a crank device that generates a linear reciprocating motion using a planetary gear mechanism composed of a gear (for example, Japanese Patent No. 2683218 (Patent Document 5)). In this crank device, the piston can reciprocate linearly without being guided by the cylinder.

Patent No. 2850054 JP 2007-177760 A JP 2006-189288 A Japanese Patent Laid-Open No. 2007-232026 Japanese Patent No. 2683218

  By the way, in a friction tester and a fatigue tester, a mechanism using a ball screw or a mechanism combining a hydraulic cylinder and a servo valve is known as a mechanism for causing a reciprocating motion to act on a device under test (for example, patent literature). 2, Patent Document 3). These can accurately cause linear reciprocation to act on the DUT. For this reason, a more accurate test result can be expected as a friction tester or a fatigue tester that causes a linear reciprocating motion to act on the DUT.

  However, from the viewpoint of the present inventor, the ball screw is not suitable for high-speed operation due to its structure when used as a mechanism for causing a linear reciprocating motion to act on the DUT. A mechanism combining a hydraulic cylinder and a servo valve is suitable for high-speed operation as compared with a ball screw, but has a limit in that the control of the servo valve is disturbed, and the speed of linear reciprocation cannot be so high. For this reason, a mechanism using a ball screw or a mechanism combining a hydraulic cylinder and a servo valve could not be tested particularly at high speed. In either case, the range of speeds allowed to maintain accuracy is not so wide, and the test cannot be performed by changing the speed greatly. In this case, a test is performed at an allowable speed, and a result when the test is performed at a high speed by calculation or the like is predicted from the result.

  Further, in an apparatus for examining the friction of a piston-cylinder mechanism used in an internal combustion engine of an automobile, a mechanism is used in which a piston is connected to a crankshaft via a connecting rod and linearly reciprocates by guiding the piston to the cylinder. (For example, patent document 4). Such a structure is effective when inspecting friction loss including so-called side thrust. However, it is not possible to measure the friction between the piston and cylinder due to the linear reciprocation of the piston.

  Further, as shown in Patent Document 5, there is a proposal of a linear reciprocating mechanism that generates a linear reciprocating motion by using a planetary gear mechanism constituted by an internal sun gear and an external planetary gear. However, no proposal has been made to use such a linear reciprocating mechanism in a testing machine such as a friction testing machine or a fatigue testing machine.

  Therefore, the present inventor proposes a new testing machine for a testing machine equipped with a mechanism for causing a linear reciprocating motion to act on a device under test such as a friction testing machine or a fatigue testing machine.

  The testing machine according to the present invention includes a linear reciprocating mechanism that causes a linear reciprocating motion to act on the DUT. A linear reciprocating mechanism of such a test machine includes a crankcase, an inner sun gear fixedly disposed on the crankcase, and a planetary gear having a pitch circle diameter that is a half of the pitch circle diameter of the inner sun gear. Is provided with a planetary gear member that rotates and revolves while meshing with the inner peripheral sun gear. Further, the linear reciprocating mechanism is disposed in the crankcase so as to rotate coaxially with the center line of the inner peripheral sun gear, and supports a planetary gear member so as to rotate and revolve, and a rotation axis direction of the planetary gear. On the pitch circle of the planetary gear as viewed from the infinity point, and an action portion that is disposed on the planetary gear member and linearly reciprocates as the crank member rotates. This linear reciprocating mechanism can cause a linear reciprocating motion to act on the DUT through the action portion. Such a testing machine can constitute a friction testing machine, a fatigue testing machine, or the like. Further, the speed of the linear reciprocating motion that acts on the DUT is wide in the range of speed that can maintain accuracy with a single testing machine, and more test conditions can be realized.

  In this case, the testing machine may include a driving device that rotates the crank member. Further, the driving device can be constituted by a servo motor, for example. When the servo motor is used, it is easy to change the speed of the linear reciprocating motion that acts on the DUT through the action portion.

  The action part may be connected to the device under test via a connecting rod. In this case, you may provide the guide part which guides so that a connecting rod may reciprocate linearly. Moreover, this guide part can be comprised with an air bearing, for example. According to such an air bearing, the connecting rod can be guided in a non-contact manner. Thereby, a linear reciprocation can be made to act stably by a to-be-tested object.

  The planetary gear member may be adjusted so that the centrifugal force acting on the planetary gear member is balanced and the moment of the centrifugal force acting on the planetary gear member is balanced at an arbitrary position on the rotation axis of the planetary gear member. In this case, the crank member may be further adjusted so that the centrifugal force acting on the crank member is balanced and the moment of the centrifugal force acting on the crank member is balanced at an arbitrary position on the rotation shaft of the crank member. In this case, vibration caused by driving the linear reciprocating mechanism can be extremely reduced.

  In this case, the planetary gear member balances the centrifugal force acting on the planetary gear member and balances the moment of the centrifugal force acting on the planetary gear member at an arbitrary position on the rotation axis of the planetary gear member. May be provided. The crank member may include a second balancer that balances the centrifugal force acting on the crank member and balances the moment of the centrifugal force acting on the crank member at an arbitrary position on the rotation shaft of the crank member. Good.

  The 1st balancer or the 2nd balancer may be attached so that exchange is possible. In this case, you may comprise a 1st balancer so that an attachment position can be changed to radial direction with respect to the rotating shaft of a planetary gear member. Moreover, you may comprise a 1st balancer so that an attachment position can be changed to an axial direction with respect to the rotating shaft of a planetary gear member. Further, the first balancer may be attached to an end portion in the axial direction of the planetary gear member.

  Further, the second balancer may be capable of changing the mounting position in the radial direction with respect to the rotation shaft of the crank member. In this case, the mounting position of the second balancer may be changed in the axial direction with respect to the rotation shaft of the crank member.

  The testing machine also includes a linear reciprocating mechanism that linearly reciprocates the DUT with respect to the flat plate, moves the DUT while pressing the DUT against the flat plate, and moves to inspect the movement resistance between the DUT and the flat plate. Applicable to resistance testing machine. Such a testing machine can be applied to a fatigue testing machine equipped with a linear reciprocating mechanism that applies a force accompanying a linear reciprocating motion to the DUT.

The mechanism figure which shows the movement resistance testing machine which concerns on one Embodiment of this invention. The side view which shows the linear reciprocation mechanism of the movement resistance testing machine which concerns on one Embodiment of this invention. (A) is a side view of a planetary gear member, (b) is a front view of the planetary gear member. The figure which shows the balance of a planetary gear member. (A) is a side view of a crank member, (b) is a front view of a crank member. The side view which shows the state which assembled | attached the planetary gear member to the crank member. The figure which shows the balance of a crank member. The mechanism figure which shows the fatigue testing machine which concerns on one Embodiment of this invention.

  Hereinafter, a testing machine including a linear reciprocating mechanism according to an embodiment of the present invention will be described with reference to the drawings.

  Here, as such a testing machine, for example, as shown in FIG. 1, a moving resistance testing machine 300 that moves the DUT 310 while pressing it against the flat plate 320 and inspects the moving resistance between the DUT 310 and the flat plate 320. Can be configured. Here, the DUT 310 is linearly reciprocated with respect to the flat plate 320 by the linear reciprocating mechanism 100. The linear reciprocating mechanism 100 will be described later in detail.

  The movement resistance tester 300 includes a pressing mechanism 330 that presses the DUT 310 against the flat plate 320. The pressing mechanism 330 may be a hydraulic mechanism capable of adjusting the pressure. Further, a required weight (weight) may be placed on the DUT 310 instead of the pressing mechanism 330.

  The flat plate 320 is a member that receives a reaction force when the DUT 310 moves, and is connected to a force detector 340 to detect a reaction force when the DUT 310 moves. For example, a load cell can be used as the force detector 340. In this embodiment, the flat plate 320 is placed on the plurality of rollers 360, and a reaction force when the DUT 310 moves acts on the force detector 340. In addition, the DUT 310 may be configured to move on the flat plate 320 via wheels, or may be configured to slide on the flat plate 320. The movement resistance tester 300 can be configured as a friction tester that, for example, slides various materials while pressing against a predetermined flat plate and obtains a friction coefficient of the material from the detected resistance value. In this case, various materials may be selected for the DUT 310 and the flat plate 320. Further, the DUT 310 may be a rolling test article, and for example, it may constitute a testing machine that performs a tire wear test or a wheel or axle durability test.

  Here, as shown in FIG. 1, the linear reciprocating mechanism 100 includes a crankcase 101, an inner peripheral sun gear 102, a planetary gear member 103, a crank member 104, and an action portion 147. The linear reciprocating mechanism 100, which will be described in detail later, uses a mechanism that generates a linear reciprocating motion using a planetary gear mechanism constituted by an internal sun gear and an external planetary gear. The linear reciprocating mechanism 100 can reciprocate the action portion 147 by driving the crank member 104 to rotate. According to such a linear reciprocating mechanism, the action portion 147 can be accurately reciprocated along a straight line, and the action portion 147 is more effective than other mechanisms such as a mechanism using a ball screw and a mechanism using a hydraulic cylinder. The speed at which the part 147 is linearly reciprocated can be increased, and the allowable range of speed change is large.

  Hereinafter, the linear reciprocating mechanism 100 will be described.

≪Linear reciprocating mechanism 100≫
In FIG. 1, such a linear reciprocating mechanism 100 and a movement resistance tester 300 are schematically shown. In this embodiment, the linear reciprocating mechanism 100 includes a crankcase 101, an inner peripheral sun gear 102, a planetary gear member 103, and a crank member 104, as shown in FIG. In FIG. 1, the mechanism of the linear reciprocating mechanism 100 is schematically shown with the right side surface of the crankcase 101 in FIG.

≪Crankcase 101≫
The crankcase 101 is a case that accommodates each member of the linear reciprocating mechanism 100. In this embodiment, the crankcase 101 is a cylindrical member having a bottom. In FIG. 2, the crankcase 101 is disposed laterally with the bottom 111 facing the left side and the opening 112 facing the right side. Inside the crankcase 101, spaces for accommodating the members of the linear reciprocating mechanism 100 such as the crank member 104 and the inner peripheral sun gear 102 are formed. An insertion hole 113 through which the shaft portion 158 of the crank member 104 is inserted is formed at the center of the bottom portion 111 of the crankcase 101. Bearings 163 and 164 for rotatably supporting the crank member 104 are provided at the opening 112 and the bottom 111 of the crankcase 101, respectively. Further, an inner peripheral sun gear 102 is fixed at an intermediate position in the axial direction of the crankcase 101.

≪Inner sun gear 102≫
The inner peripheral sun gear 102 is an internal gear having teeth on the inner peripheral surface. In this embodiment, the inner peripheral sun gear 102 is fixed to a step 121 formed at an intermediate position on the inner peripheral surface of the crankcase 101.

≪Planetary gear member 103≫
The planetary gear member 103 is a member that rotates and revolves by meshing with the inner peripheral sun gear 102. FIG. 3A is a side view showing the planetary gear member 103 of this embodiment. The planetary gear member 103 includes a planetary gear 131 and a planetary shaft 132 as shown in FIG.

  The planetary gear 131 is an external gear having teeth on the outer peripheral surface, and has a pitch circle diameter that is a half of the pitch circle diameter of the inner peripheral sun gear 102 as shown in FIG. That is, the ratio between the radius r1 of the pitch circle 103c of the planetary gear member 103 and the radius r2 of the pitch circle 102c of the inner peripheral sun gear 102 is such that r1: r2 = 1: 2. As shown in FIG. 3A, a mounting hole 141 is formed at the center of the planetary gear 131 and is mounted on the planetary shaft 132.

  As shown in FIG. 3, the planetary shaft 132 includes a mounting shaft portion 146 to which the planetary gear 131 is mounted, an action portion 147, a first counterweight 148, and a first balancer 149.

  The mounting shaft portion 146 is a portion that is mounted on the planetary gear 131 and is provided at one end of the planetary shaft 132. A planetary gear 131 is mounted on the mounting shaft portion 146. Although not shown, the mounting shaft portion 146 has a spline or key engagement. Thereby, the planetary gear 131 is mounted so as not to rotate with respect to the planetary shaft 132.

  The first balancer 149 balances the centrifugal force acting on the planetary gear member 103 and balances the moment of the centrifugal force acting on the planetary gear member 103 at an arbitrary position on the rotation axis c2 of the planetary gear member 103. It is. In this embodiment, the first balancer 149 is attached in a replaceable manner, and is attached to the end surface of the mounting shaft portion 146 with a screw 150. As shown in FIGS. 3A and 3B, the first balancer 149 includes a base portion 149a attached to the end surface of the mounting shaft portion 146 and a substantially fan-shaped weight portion 149b. In this embodiment, the first balancer 149 is attached so that the center of the arc of the fan-shaped weight portion 149 b is the rotation axis c <b> 2 of the planetary gear member 103. The base 149a is provided with a protrusion 149c that engages with the planetary gear 131 and prevents rotation.

  Thus, the first balancer 149 is provided at one end of the planetary shaft 132. An action part 147 and a first counterweight 148 are provided at the opposite end of the planetary shaft 132.

  As shown in FIGS. 1 and 3, the action portion 147 is disposed on the pitch circle 103c of the planetary gear 131 (on the pitch circle 103c of the planetary gear 131 as viewed from the infinity point). In this embodiment, the action part 147 is a pin-shaped member, and is provided so that the central axis c3 is orthogonal to the pitch circle 103c. As shown in FIGS. 1 and 2, a connecting rod 305 connected to the DUT 310 is connected to the action portion 147.

  The first counterweight 148 generates an inertia force of rotation of the planetary gear member 103. In this embodiment, as shown in FIGS. 3A and 3B, the first counterweight 148 is a substantially semicircular arc-shaped member, and is provided by being shifted in the radial direction from the rotation axis c <b> 2 of the planetary gear member 103. ing. Further, the center of gravity of the first counterweight 148 is provided at a position that is shifted 180 degrees in the circumferential direction from the central axis c3 of the action portion 147 with the rotation axis c2 of the planetary gear member 103 as the center.

≪Balance of planetary gear member 103≫
FIG. 4 is a diagram schematically showing the balance of the planetary gear member 103. In this embodiment, the planetary gear member 103 is composed of a planetary gear 131 and a planetary shaft 132 as shown in FIG. 2, and the action member 147 has an operating member 200 (in this embodiment, a connecting rod 305 and a covered shaft). A test article 310) is attached. The planetary gear member 103 adjusts the balance so that the centrifugal force acting on the planetary gear member 103 is balanced and the moment of the centrifugal force acting on an arbitrary position on the rotational axis c2 of the planetary gear member 103 is balanced. ing. That is, the planetary gear member 103 can be modeled as shown in FIG. In FIG. 4, c2 is a rotation shaft of the planetary gear member 103, M1 is a mass body corresponding to the DUT 310 connected to the action portion 147, M2 is a mass body corresponding to the first counterweight 148, M3 Indicates mass bodies corresponding to the first balancer 149, respectively.

  In the model shown in FIG. 4, when the planetary gear member 103 rotates, the centrifugal force acting on the mass body M1 (the operation member 200) is F1, and the centrifugal force acting on the mass body M2 (the first counterweight 148) is F2. The centrifugal force acting on the mass body M3 (first balancer 149) is defined as F3. This planetary gear member 103 balances centrifugal force F1, centrifugal force F2, and centrifugal force F3 (F1 + F2 + F3 = 0 (F1, F2, and F3 are vector quantities)).

In this case, F1, F2, and F3 can each be calculated by the formula “centrifugal force = mass × radius × (angular velocity) ² ”, and the directions of the centrifugal forces F1, F2, and F3 are radial with respect to the rotation axis c2. Acts outward. (Angular velocity) ² can be removed because it is common to each term, and the size of each term of F1, F2, and F3 can be replaced by mass × radius. Furthermore, in this embodiment, as shown in FIG. 2, the operating member 200 and the first balancer 149 are disposed with a 180 ° shift in the circumferential direction with respect to the first counterweight 148. Therefore, the centrifugal force F1 acting on the mass body M1 (operation member 200) and the centrifugal force F3 acting on the mass body M3 (first balancer 149) are the centrifugal forces acting on the mass body M2 (first counterweight 148). The direction is always opposite to F2. Therefore, in this embodiment, the mass of the mass body M1 (operation member 200) is m1, the radial distance is A1, the mass of the mass body M2 (first counterweight 148) is m2, the radial distance is A2, and the mass body M3. When the mass of the (first balancer 149) is m3 and the radial distance is A3, F1 + F2 + F3 = 0 (F1, F2, and F3 are vector quantities) is (m1 × A1 + m3 × A3) − (m2 × A2) = 0 It becomes. As described above, when the planetary gear member 103 rotates with the operation member 200 attached to the action portion 147, the centrifugal force acting on the planetary gear member 103 is balanced.

  Furthermore, in this embodiment, the moment of the centrifugal force (F1, F2, F3) acting on the planetary gear member 103 is balanced at an arbitrary position on the rotation axis c2 of the planetary gear member 103.

  That is, as shown in FIG. 4, the axial distances from the arbitrary position O1 on the rotation axis c2 of the planetary gear member 103 to the positions where the centrifugal forces F1, F2, and F3 act are L1, L2, and L3, respectively. To do. The planetary gear member 103 has F1 × L1 + F2 × L2 + F3 × L3 = 0 (F1, F2, and F3 are vector quantities). Thereby, when the planetary gear member 103 rotates, the force acting to rotate the planetary gear member 103 around an axis orthogonal to the rotation axis c2 at an arbitrary position on the rotation axis c2 can be suppressed to a small value. it can.

  In this embodiment, as described above, the planetary gear member 103 includes F1 + F2 + F3 = 0 (F1, F2, and F3 are vector quantities) and F1 × L1 + F2 × L2 + F3 × L3 = 0 (F1, F2, and F3 are vector quantities). ), The weight of the first balancer 149 is adjusted. In practice, manufacturing tolerances occur with respect to the weight and mounting position of each member. For this reason, when adjusting the weight of the first balancer 149, for example, a dummy weight corresponding to the operation member 200 is disposed in the operating portion 147, and the state is the same as the state supported by the crank member 104. The planetary gear member 103 is rotatably supported. Then, the planetary shaft 132 is rotated by a motor or the like, and the weight and the mounting position of the first balancer 149 may be finely adjusted so that the vibration generated in the planetary gear member 103 is reduced.

  In this embodiment, the first balancer 149 is attached to the axial end of the planetary gear member 103. In other words, in this embodiment, the first balancer 149 is attached to the end of the planetary gear member 103 that is axially separated from the position where the action portion 147 and the first counterweight 148 are attached. In this case, the position where the first balancer 149 is attached is farthest in the axial direction from the position where the action part 147 and the first counterweight 148 are attached. For this reason, the moment of the centrifugal force that acts on the planetary gear member 103 by the first balancer 149 is large in the vicinity of the action portion 147 and the first counterweight 148. For this reason, when attaching the 1st balancer 149 to the planetary gear member 103 with the same radial distance from the rotating shaft c2 of the planetary gear member 103, the 1st balancer 149 can be made lightest compared with the other position of the planetary gear member 103. . In this way, by attaching the first balancer 149 to the shaft end portion of the planetary gear member 103, the first balancer 149 can be reduced, so that the entire linear reciprocating mechanism 100 can be reduced.

  When the planetary gear member 103 is rotated, the centrifugal force acting on the planetary gear member 103 is balanced, and the moment of the centrifugal force acting on an arbitrary position on the rotation axis of the planetary gear member 103 is balanced. An example is shown in the model shown in FIG. For example, in the model shown in FIG. 4, the mass body M1, the mass body M2, and the mass body M3 have the same radial distance (A1, A2, A3) from the rotation axis c2 to the center of gravity. The mass body M1 is disposed on the right side s and the mass body M3 is disposed on the left side at a distance of 2s from the position where the mass body M2 is attached to the rotation shaft c2. In this case, for example, when the mass body M1 is 2 g, the mass body M2 is 3 g, and the mass body M3 is 1 g, the centrifugal forces F1, F2, and F3 acting on the planetary gear member 103 are balanced, and the planetary gear member 103 The moments of the centrifugal forces F1, F2, and F3 acting on arbitrary positions on the rotation axis c2 of these are balanced. An example in which the centrifugal force acting on the planetary gear member 103 is balanced and the moment of the centrifugal force acting on an arbitrary position on the rotation axis c2 of the planetary gear member 103 is balanced is not limited to this example. In an actual machine, since the weight of each member is slightly different, the centrifugal forces F1, F2, and F3 acting on the planetary gear member 103 are balanced, and the centrifugal force acting on an arbitrary position on the rotation axis c2 of the planetary gear member 103. The balance may be adjusted for each actual machine so that the moments of F1, F2, and F3 are balanced.

≪Crank member 104≫
Next, the crank member 104 in the linear reciprocating mechanism 100 will be described. As shown in FIG. 2, the crank member 104 is disposed in the crankcase 101 so as to rotate coaxially with the center line c <b> 1 of the inner peripheral sun gear 102. The crank member 104 supports the planetary gear member 103 so that it can rotate and revolve. FIG. 5 is a side view of the crank member 104. FIG. 6 is a side view showing a state in which the planetary gear member 103 is incorporated in the crank member 104.

  In this embodiment, as shown in FIG. 5A, the crank member 104 is a shaft member that is thick on one side and thin on the opposite side. As shown in FIGS. 5A and 5B, a mounting hole 152 for mounting the above-described planetary gear member 103 is formed in the thick shaft portion 151 on one side. The center line of the mounting hole 152 is offset from the rotation axis c1 of the crank member 104 by a distance r1 of the pitch circle 103c of the planetary gear 131, and coincides with the center line c2 of the pitch circle 103c of the planetary gear 131. Further, the intermediate portion of the crank member 104 is formed slightly thinner than the thick shaft portion 151. In the intermediate portion, the bottom portion of the mounting hole 152 formed in the thick shaft portion 151 is open to the side surface of the crank member 104 as indicated by 152a in the figure.

  In this embodiment, a second counterweight 159 and a second balancer 160 are attached to the crank member 104. The second counterweight 159 is attached to one end surface of the crank member 104 where the thick shaft portion 151 is formed. The second counterweight 159 is a mass member having a substantially semicircular arc shape corresponding to the end face of the crank member 104. At the center of the arc, an arc-shaped notch 159a centering on the center line c2 of the mounting hole 152 is formed.

  The second balancer 160 is a member that balances the centrifugal force acting on the crank member 104 and balances the moment of the centrifugal force acting on the crank member 104 at an arbitrary position on the rotation axis c <b> 1 of the crank member 104. In this embodiment, as shown in FIG. 2, the crank member 104 has a shaft portion 158 that is inserted into the insertion hole 113 of the crankcase 101 and is rotatable with respect to the crankcase 101 via bearings 163 and 164. It is installed. In this embodiment, a flywheel 170 is attached to the shaft portion 158 of the crank member 104 that extends outside the crankcase 101. The second balancer 160 is attached at a position away from the rotation center of the flywheel 170 in the radial direction.

<< Attachment structure of planetary gear member 103 and crank member 104 >>
In this embodiment, as shown in FIG. 2, the planetary gear member 103 is rotatably mounted in the mounting hole 152 of the crank member 104 with bearings 161 and 162 interposed therebetween. Specifically, the planetary gear member 103 is mounted in the mounting hole 152 in a state in which the first counterweight 148 and the action portion 147 protrude from the mounting hole 152 of the crank member 104. As shown in FIGS. 2 and 6, the mounting shaft portion 146 of the planetary shaft 132 reaches the opening 152 a at the bottom of the mounting hole 152 of the crank member 104. The tooth surface of the planetary gear 131 attached to the mounting shaft portion 146 is exposed to the outside of the crank member 104 from the opening 152 a at the bottom of the mounting hole 152 of the crank member 104.

  The second counterweight 159 attached to the end face of the crank member 104 is formed with an arc-shaped notch 159a centering on the center line c2 of the mounting hole 152, as shown in FIG. For this reason, even if the planetary gear member 103 rotates, the first counterweight 148 and the action portion 147 do not interfere with the second counterweight 159.

≪Mounting structure to crankcase 101≫
The planetary gear member 103 and the crank member 104 are attached to the crankcase 101 as shown in FIG. The crank member 104 is rotatably mounted on the crankcase 101 with bearings 163 and 164 interposed therebetween. The crank member 104 is mounted so as to rotate coaxially with the center line c1 of the pitch circle 102c of the inner peripheral sun gear 102 fixed to the crankcase 101. The planetary gear 131 is exposed from the opening 152 a at the bottom of the mounting hole 152 of the crank member 104 and meshes with the inner peripheral sun gear 102.

  As shown in FIG. 2, the movement resistance tester 300 may include a driving device 220 that rotates the crank member 104. In this embodiment, a servo motor is used as the driving device 220. In other words, the crank member 104 of the linear reciprocating mechanism 100 is transmitted with power for driving the linear reciprocating mechanism 100 from the servo motor 220 to the shaft portion 158 of the crank member 104. As a result, the crank member 104 rotates. When the crank member 104 rotates, the planetary gear member 103 rotates and revolves while meshing with the inner peripheral sun gear 102.

≪Section trajectory≫
That is, the planetary gear member 103 is supported by bearings 163 and 164 mounted in the mounting holes 152 of the crank member 104 as shown in FIGS. The planetary gear member 103 meshes with the inner peripheral sun gear 102 and revolves while rotating according to the rotation of the crank member 104. In the linear reciprocating mechanism 100, as shown in FIG. 1, the ratio between the radius r1 of the pitch circle 103c of the planetary gear 131 and the radius r2 of the pitch circle 102c of the inner peripheral sun gear 102 is r1: r2 = 1: 2. It has become a relationship. For this reason, the planetary gear member 103 rotates twice every revolution.

  The action part 147 that protrudes in the axial direction from the planetary shaft 132 of the planetary gear member 103 is disposed at a position that is radially displaced from the rotation axis c2 of the planetary gear member 103 by the radius r1 of the pitch circle 103c. As described above, the ratio between the radius r1 of the pitch circle 103c of the planetary gear 131 and the radius r2 of the pitch circle 102c of the inner peripheral sun gear 102 is such that r1: r2 = 1: 2. Furthermore, the action part 147 is disposed on the pitch circle 103c of the planetary gear 131 when viewed from the infinity point in the direction of the rotation axis c2 of the planetary gear 131. For this reason, this action part 147 linearly reciprocates along the diameter of the pitch circle 102 c of the inner peripheral sun gear 102 in accordance with the rotation and revolution of the planetary gear member 103.

  Schematically, as shown in FIG. 1, when the crank member 104 rotates in the direction of the arrow e in the figure, the planetary gear member 103 rotates in the direction of the arrow f, and the action part 147 moves along the straight line L. Move in the direction of arrow g. When the crank member 104 rotates in the reverse direction, the rotation direction of the planetary gear member 103 is also reversed, and the action portion 147 moves along the straight line L in the direction opposite to the arrow g.

  In this embodiment, a connecting rod 305 is attached to the action portion 147. As shown in FIG. 2, the connecting rod 305 is connected so as to be orthogonal to the action portion 147. The connecting rod 305 extends along a straight line L along which the action portion 147 reciprocates linearly.

  A device under test 310 of the moving resistance tester 300 is attached to the tip of the connecting rod 305. Here, the linear reciprocating mechanism 100 is arranged at a predetermined position so that the straight line L on which the action portion 147 reciprocates linearly follows a straight line on which the object to be tested 310 is reciprocated in the moving resistance tester 300. . Thereby, the DUT 310 can be appropriately reciprocated along the predetermined straight line L. In this case, the stroke amount of the DUT 310 can be adjusted by increasing or decreasing the pitch circle 102c of the inner peripheral sun gear 102 and the pitch circle 103c of the planetary gear 131.

  In this embodiment, the linear reciprocating mechanism 100 balances the centrifugal force acting on the crank member 104 and balances the moment of the centrifugal force acting on an arbitrary position on the rotation axis c1 of the crank member 104. That is, the linear reciprocating mechanism 100 can be modeled as shown in FIG. In FIG. 7, c1 is a rotation shaft of the crank member 104, M11 is a mass body corresponding to the planetary gear member 103, M12 is a mass body corresponding to the second counterweight 159, and M13 is equivalent to the second balancer 160. Each mass is shown.

  In the model shown in FIG. 7, when the crank member 104 rotates, the centrifugal force acting on the mass body M11 (planetary gear member 103) is F11, and the centrifugal force acting on the mass body M12 (second counterweight 159) is F12. The centrifugal force acting on the mass body M13 (second balancer 160) is defined as F13. This crank member 104 balances centrifugal force F11, centrifugal force F12, and centrifugal force F13 (F11 + F12 + F13 = 0 (F11, F12, and F13 are vector quantities)). Further, in this embodiment, the moment of the centrifugal force (F11, F12, F13) acting on the crank member 104 is balanced at an arbitrary position on the rotation axis c1 of the crank member 104.

  That is, as shown in FIG. 7, the axial distances from the arbitrary position O2 on the rotation axis c1 of the crank member 104 to the positions at which the centrifugal forces F11, F12, and F13 act are L11, L12, and L13, respectively. . The crank member 104 has F11 × L11 + F12 × L12 + F13 × L13 = 0 (F11, F12, and F13 are vector quantities). As a result, when the crank member 104 rotates, the force acting to rotate the crank member 104 around an axis orthogonal to the rotation axis c1 at an arbitrary position on the rotation axis c1 can be kept small.

  In this embodiment, as described above, the crank member 104 has F11 + F12 + F13 = 0 (F11, F12, and F13 are vector quantities) and F11 × L11 + F12 × L12 + F13 × L13 = 0 (F11, F12, and F13 are vector quantities). Thus, the weight of the second balancer 160 is adjusted. Actually, for each member, manufacturing tolerances occur in terms of weight and mounting position. When adjusting the weight of the second balancer 160, a dummy weight corresponding to the planetary gear member 103 is disposed on the crank member 104, and the crank member 104 is rotated in the same state as that supported by the crankcase 101. Support freely. Then, the weight and the mounting position of the second balancer 160 may be finely adjusted so that the crank member 104 is rotated by a motor or the like, and vibration generated in the crank member 104 is reduced.

  In this embodiment, the second balancer 160 is attached to the flywheel 170. Since the flywheel 170 is separated from the rotation axis c1 of the crank member 104, the centrifugal force that acts even when the weight of the second balancer 160 is reduced increases. Therefore, the lighter second balancer 160 can balance the centrifugal force acting on the crank member 104 and balance the moment of the centrifugal force acting on an arbitrary position on the rotation axis c1 of the crank member 104.

  In the linear reciprocating mechanism 100, as described above, the centrifugal force acting on the planetary gear member 103 is balanced, and the moment of the centrifugal force acting on an arbitrary position on the rotation axis c2 of the planetary gear member 103 is balanced. Furthermore, the centrifugal force acting on the crank member 104 is balanced, and the moment of the centrifugal force acting on an arbitrary position on the rotation axis c1 of the crank member 104 is balanced. For this reason, it is possible to suppress a biased load from acting on the rotation shaft c2 of the planetary gear member 103 and the rotation shaft c1 of the crank member 104. Thereby, the vibration generated by driving the linear reciprocating mechanism 100 can be extremely reduced.

≪Movement resistance tester 300≫
In this movement resistance tester 300, the linear reciprocating mechanism 100 includes the crankcase 101, the inner peripheral sun gear 102, the planetary gear member 103, the crank member 104, and the action portion 147 as described above. . Then, the device under test 310 can be linearly reciprocated through the action portion 147. In this case, the linear reciprocation mechanism 100 can accurately linearly reciprocate the DUT 310. Further, according to the linear reciprocating mechanism 100, the speed of the DUT 310 can be increased as compared with a testing machine using other mechanisms such as a mechanism using a ball screw or a mechanism using a hydraulic cylinder. Further, since the DUT 310 can be linearly reciprocated stably even at a low speed, the DUT 310 has a degree of freedom in speed. The speed of the DUT 310 can be changed by adjusting the rotational speed applied to the crank member 104 of the linear reciprocating mechanism 100. Therefore, a desired test can be performed under various conditions.

  That is, the linear reciprocating mechanism 100 can change the speed of the DUT 310 by changing the rotation speed of the servo motor 220. As a result, the test can be performed under various conditions on the speed of the device under test 310. Therefore, a test for measuring the movement resistance of the DUT 310 when operating at a low speed and the movement resistance of the DUT 310 when operating at a high speed can be realized with a single testing machine.

  Further, the linear reciprocating mechanism 100 described above balances the centrifugal force acting on the planetary gear member 103, and the moment of the centrifugal force acting on the planetary gear member 103 at an arbitrary position on the rotation axis c2 of the planetary gear member 103. Can be balanced. Furthermore, the centrifugal force acting on the crank member 104 can be balanced, and the moment of the centrifugal force acting on the crank member 104 at any position on the rotation axis c1 of the crank member 104 can be balanced. As a result, vibration during driving can be reduced. Further, the influence of vibration caused by driving the linear reciprocating mechanism 100 can be reduced.

  The moving resistance tester 300 includes a pressing mechanism 330 that presses the DUT 310 against the flat plate 320. The moving resistance test is performed by adjusting the force that the pressing mechanism 330 acts on the DUT 310. You can change the conditions. As described above, the moving resistance tester 300 can reduce the vibration that acts on the DUT 310 from the linear reciprocating mechanism 100, so that the force of the pressing mechanism 330 acts on the DUT 310 appropriately. Can be made. Therefore, in the movement resistance tester 300, a measurement result with higher accuracy can be expected as compared with a tester using another mechanism such as a mechanism using a ball screw or a mechanism using a hydraulic cylinder.

  That is, according to the linear reciprocating mechanism 100, since vibration can be suppressed to a small value, for example, if the stroke of the DUT 310 is about 50 mm, even if the DUT 310 is operated at a speed of about 5000 rpm, Appropriate tests can be performed. On the other hand, for example, in the case of a ball screw type linear reciprocating mechanism, if the stroke of the DUT 310 is about 50 mm, the speed of about 300 rpm is the limit. In the case of a mechanism using a hydraulic cylinder and a servo valve, if the stroke of the DUT 310 is about 50 mm, a speed of about 600 rpm is the limit. As described above, the linear reciprocating mechanism 100 described above can achieve high-speed operation in the movement resistance tester 300 and can maintain accuracy even at low-speed operation. Therefore, the allowable speed range is wide while maintaining accuracy.

  As described above, the moving resistance tester 300 has a wide range of speeds with which the accuracy of the test object 310 can be maintained with a single tester, and can realize more test conditions. Moreover, since the vibration resulting from the linear reciprocating mechanism 100 can be reduced, high accuracy can be expected. Therefore, many test conditions that cannot be realized with a testing machine using another mechanism such as a mechanism using a ball screw or a mechanism using a hydraulic cylinder can be realized with a single testing machine.

  In the above-described embodiment, the preferred form of the linear reciprocating mechanism 100 is illustrated. The linear reciprocating mechanism 100 is not limited to the above-described embodiment. For example, in the above-described embodiment, the first balancer 149 and the second balancer 160 are attached to be exchangeable. Thereby, the weight and attachment position of the first balancer 149 and the second balancer 160 can be finely adjusted. However, the present invention is not limited to this, and the first balancer 149 and the second balancer 160 may be fixed to the planetary gear and the crank member, respectively. That is, even if the weights and mounting positions of the first balancer and the second balancer cannot be finely adjusted, the centrifugal force acting on the planetary gear and the crank member is balanced as described above, and the planetary gear and the crank member are also balanced. By providing the balancer designed so as to balance the moment of the centrifugal force acting on any position on the rotation axis, a temporary effect of suppressing the vibration of the linear reciprocating mechanism 100 can be obtained.

  Further, the first balancer 149 may be configured such that the attachment position can be changed in the radial direction or the axial direction with respect to the rotation axis c2 of the planetary gear 131. Accordingly, it is easy to balance the centrifugal force acting on the planetary gear 131 and balance the moment of the centrifugal force acting on an arbitrary position on the rotation axis c2 of the planetary gear 131. Further, the second balancer 160 may be configured such that the attachment position can be changed in the radial direction or the axial direction with respect to the rotation axis c1 of the crank member 104. Accordingly, it is easy to balance the centrifugal force acting on the crank member 104 and balance the moment of the centrifugal force acting on an arbitrary position on the rotation axis c1 of the crank member 104. If the vibration is sufficiently suppressed without using the first balancer 149 and the second balancer 160, the first balancer 149 and the second balancer 160 may not be used.

  The specific shapes and structures of the inner sun gear 102, the planetary gear member 103, the crankcase 101, the crank member 104, and the like described above can be variously changed. Further, in the present embodiment, the configuration in which the action portion is connected to the connecting rod so as to be rotatable is illustrated, but such a configuration is merely an example of the present invention.

  As described above, with respect to a testing machine having a linear reciprocating mechanism that causes a linear reciprocating motion to act on the DUT, the DUT 310 is moved while being pressed against the flat plate 320, and the movement resistance between the DUT 310 and the flat plate 320 is inspected. The movement resistance tester 300 has been described as an example. Note that the testing machine provided with the linear reciprocating mechanism that causes the test object to perform the linear reciprocating motion is not limited to the moving resistance testing machine 300.

  For example, a testing machine equipped with a linear reciprocating mechanism that causes a linear reciprocating motion to act on the DUT can further constitute a fatigue testing machine 400 as shown in FIG. In this case, it is preferable to apply a force accompanying the linear reciprocation to the DUT 410 via the linear reciprocation mechanism 100. In this embodiment, the fatigue testing machine 400 will be described by taking a fatigue testing machine that repeatedly applies shear deformation to the rubber material 410 as an example. In this case, the rubber material 410 may be sandwiched between a pair of flat plates 420 and 430 arranged in parallel and bonded to the pair of flat plates 420 and 430, respectively.

  One flat plate 420 is connected to the operating portion 147 of the linear reciprocating mechanism 100 via a connecting rod 405, and the one flat plate 420 is relatively reciprocated linearly with respect to the other flat plate 430 while maintaining parallelism. Good. In this embodiment, the load applied to the flat plate 420 is measured by the load cell 440. In addition, the counter 460 counts the number of times the shear force is applied. For example, the counter 460 may measure the number of rotations of the crank member 104 of the linear reciprocating mechanism 100. In this case, it is possible to measure how many times the shear force is applied before the rubber material 410 is cracked or broken.

  According to the fatigue testing machine 400, the linear reciprocating mechanism 100 includes the crankcase 101, the inner peripheral sun gear 102, the planetary gear member 103, the crank member 104, and the action portion 147, as shown in FIG. And the DUT 410 can be reciprocated linearly through the action portion 147. Also in this case, the linear reciprocating mechanism 100 can change the speed of the DUT 410 by changing the rotation speed of a servo motor (not shown). Thereby, it is possible to perform the test while changing various conditions for the speed of the DUT 410. In the fatigue test, the shear force may increase to several hundred thousand times. According to the fatigue testing machine 400, the speed of the linear reciprocating mechanism 100 can be increased, so that the time required for the test can be considerably shortened. Thus, the linear reciprocating mechanism 100 described above is also suitable for such a fatigue tester 400.

  The fatigue tester 400 has been described above with an example, but the fatigue tester 400 is not limited to the above form. For example, the DUT 410 is not limited to the rubber material 410 described above, and various materials can be used as the DUT 410. Further, it can be applied not only to a shear deformation test but also to a bending test, a tensile compression test, and the like.

  Moreover, various forms 300 and 400 were illustrated as a testing machine provided with the linear reciprocation mechanism which makes a to-be-tested object act | operate a linear reciprocation. In this case, the action part 147 is connected to the device under test 310 and the device under test 410 via connecting rods 305 and 405, respectively. In this case, for example, as shown in FIGS. 1 and 8, guide portions 306 and 406 for guiding the connecting rods 305 and 405 so as to reciprocate linearly may be provided. In this case, the guide portions 306 and 406 may be constituted by a slide bearing or an air bearing. In the case of the air bearings 306 and 406, for example, an exterior member that covers the outer periphery of the connecting rods 305 and 405, and compressors 306b and 406b that supply compressed air between the exterior members 306a and 406a and the connecting rods 305 and 405, You may comprise.

  According to the air bearings 306 and 406, the connecting rods 305 and 405 can be guided in a non-contact manner. Further, by providing such guide portions 306 and 406, the trajectory of the action portion 147 of the linear reciprocating mechanism 100 may deviate from a predetermined straight line L due to, for example, an error in installing the linear reciprocating mechanism 100. Even in this case, the trajectories of the connecting rods 305 and 405 can be appropriately corrected. As a result, in a testing machine equipped with a linear reciprocating mechanism that causes a linear reciprocating motion to act on the DUT, the linear reciprocating motion can be stably applied to the DUT.

  As described above, the testing machine according to the present invention includes the linear reciprocating mechanism 100 that causes linear reciprocation to act on the device under test 310 and the device under test 410, for example, as shown in FIG. 1 or FIG. As described above, the linear reciprocating mechanism 100 includes the crank member 104, the inner peripheral sun gear 102 fixedly disposed on the crank member 104, and a pitch that is a half of the pitch circle diameter of the inner peripheral sun gear 102. A planetary gear member 103 that rotates and revolves while meshing with a planetary gear 131 having a circular diameter with an inner peripheral sun gear 102 is provided. Further, the linear reciprocating mechanism 100 is disposed in the crankcase 101 so as to rotate coaxially with the center line of the inner peripheral sun gear 102, and supports a planetary gear member 103 so that it can rotate and revolve, and a planetary gear. An action portion 147 disposed on the planetary gear member 103 on the pitch circle of the planetary gear 131 when viewed from an infinite point in the rotation axis direction of the gear 131 and linearly reciprocating as the crank member 104 rotates. Yes. Then, linear reciprocation is applied to the DUTs 310 and 410 through the action part 147.

  According to this linear reciprocating mechanism 100, the operation portion 147 can be linearly reciprocated by rotating the crank member 104. In this case, there is a degree of freedom in the speed of linear reciprocation applied to the DUTs 310 and 410, and a desired test can be performed under various conditions for the linear reciprocation applied to the DUTs 310 and 410. As described above, in the testing machine according to the present invention, the speed of the linear reciprocating motion that acts on the DUT also has a wide range of speeds that can maintain accuracy with a single testing machine, and realizes more test conditions. it can. Therefore, many test conditions that cannot be realized with a testing machine using another mechanism such as a mechanism using a ball screw or a mechanism using a hydraulic cylinder can be realized with a single testing machine.

  In the above embodiment, examples of the movement resistance tester 300 (see FIG. 1) and the fatigue tester 400 (see FIG. 8) are given as the tester according to the present invention, but the tester according to the present invention is The present invention is not limited to these, and can be applied to various testing machines provided with a linear reciprocating mechanism that causes a linear reciprocating motion to act on the DUT. For example, although not shown, a sliding resistance tester for measuring the sliding resistance between the cylinder and the piston can be configured. In this case, for example, a piston may be linearly reciprocated with respect to the cylinder by a linear reciprocating mechanism, and at this time, a force acting on the cylinder may be detected. The linear reciprocating mechanism can reciprocate the DUT at a speed of, for example, about 10 m / s. For this reason, an impact tester can also be comprised by comprising so that an impact may be given to another member with such a to-be-tested object.

  As mentioned above, although various embodiment which concerns on this invention was illustrated about the testing machine provided with the linear reciprocation mechanism which acts on a to-be-tested object, this invention is not limited to embodiment illustrated above.

DESCRIPTION OF SYMBOLS 100 Linear reciprocation mechanism 101 Crankcase 102 Inner peripheral sun gear 102c Pitch circle 103 Planetary gear member 103c Pitch circle 104 Crank member 111 Bottom part 112 Opening 113 Insertion hole 121 Step 131 Planetary gear 132 Planetary shaft 141 Mounting hole 146 Mounting shaft part 147 Action part 148 First counterweight 149 First balancer 149a Base 149b Weight 149c Protrusion 151 Shaft 152 Mounting hole 152a Opening 158 Shaft 159 Second counterweight 160 Second balancer 161, 162 Bearing 163, 164 Bearing 170 Flywheel 200 Operating member 220 Servo motor (drive device)
300 Movement resistance tester 305 Connecting rod 306, 406 Air bearing (guide part)
306a, 406a Exterior member 306b, 406b Compressor 310 DUT 320 Flat plate 330 Pressing mechanism 340 Force detector 360 Roller 400 Fatigue testing machine 405 Connecting rod 410 Rubber material (DUT)
420, 430 Flat plate 440 Load cell 460 Counter

Claims (16)

In a testing machine equipped with a linear reciprocating mechanism that causes a linear reciprocating motion to act on the DUT,
The linear reciprocating mechanism is
A crankcase,
An inner sun gear fixedly disposed on the crankcase;
A planetary gear member that rotates and revolves while meshing a planetary gear having a pitch circle diameter of half the pitch circle diameter of the inner circumferential sun gear with the inner circumferential sun gear;
A crank member disposed in the crankcase so as to rotate coaxially with a center line of the inner peripheral sun gear, and supporting the planetary gear member so as to be capable of rotating and revolving;
An action portion that is disposed on the planetary gear member on the pitch circle of the planetary gear as viewed from an infinite point in the rotational axis direction of the planetary gear, and linearly reciprocates with the rotation of the crank member;
A testing machine provided with a linear reciprocating mechanism that causes a linear reciprocating motion to act on the DUT through the action part.   The testing machine provided with the linear reciprocation mechanism described in Claim 1 provided with the drive device which rotationally drives the said crank member.   3. The testing machine having a linear reciprocating mechanism according to claim 2, wherein the driving device is a servo motor. The action part is connected to the DUT via a connecting rod,
The testing machine provided with the linear reciprocation mechanism as described in any one of Claim 1 to 3 provided with the guide part which guides the said connecting rod so that it may reciprocate linearly.   The testing machine provided with the linear reciprocating mechanism according to claim 4, wherein the guide portion is configured by an air bearing. The planetary gear member balances the centrifugal force acting on the planetary gear member, and balances the moment of centrifugal force acting on the planetary gear member at an arbitrary position on the rotational axis of the planetary gear member,
6. The crank member according to claim 1, wherein centrifugal force acting on the crank member is balanced, and moment of centrifugal force acting on the crank member is balanced at an arbitrary position on a rotation shaft of the crank member. A testing machine provided with the linear reciprocating mechanism described in any one of the items.   The planetary gear member balances the centrifugal force acting on the planetary gear member and balances the moment of the centrifugal force acting on the planetary gear member at an arbitrary position on the rotation axis of the planetary gear member. The testing machine provided with the linear reciprocation mechanism of Claim 6 provided with the balancer.   The crank member includes a second balancer that balances the centrifugal force acting on the crank member and balances the moment of the centrifugal force acting on the crank member at an arbitrary position on the rotation shaft of the crank member. A testing machine comprising the linear reciprocating mechanism according to claim 6.   The testing machine provided with the linear reciprocation mechanism according to claim 7 or 8, wherein the first balancer or the second balancer is attached to be exchangeable.   The testing machine provided with the linear reciprocation mechanism according to claim 7, wherein the first balancer is capable of changing a mounting position in a radial direction with respect to a rotation shaft of the planetary gear member.   The testing machine having a linear reciprocation mechanism according to claim 7, wherein the first balancer can be attached in an axial direction with respect to a rotation axis of the planetary gear member.   The test machine equipped with the linear reciprocating mechanism according to claim 7, wherein the first balancer is attached to an axial end portion of the planetary gear member.   The test machine equipped with the linear reciprocating mechanism according to claim 8, wherein the second balancer is capable of changing a mounting position in a radial direction with respect to a rotation shaft of the crank member.   The test machine equipped with the linear reciprocating mechanism according to claim 8, wherein the second balancer can change an attachment position in an axial direction with respect to a rotation shaft of a crank member. A moving resistance testing machine is provided with a linear reciprocating mechanism for linearly reciprocating the DUT with respect to the flat plate, moving the DUT while pressing it against the flat plate, and inspecting the movement resistance between the DUT and the flat plate And
The linear reciprocating mechanism is
A crankcase,
An inner sun gear fixedly disposed on the crankcase;
A planetary gear member that rotates and revolves while meshing a planetary gear having a pitch circle diameter of half the pitch circle diameter of the inner circumferential sun gear with the inner circumferential sun gear;
A crank member disposed in the crankcase so as to rotate coaxially with a center line of the inner peripheral sun gear, and supporting the planetary gear member so as to be capable of rotating and revolving;
An action portion that is disposed on the planetary gear member on the pitch circle of the planetary gear as viewed from an infinite point in the rotational axis direction of the planetary gear, and linearly reciprocates with the rotation of the crank member;
With
A movement resistance tester that linearly reciprocates the DUT with respect to the flat plate through the action portion. A fatigue testing machine equipped with a linear reciprocating mechanism that applies a force accompanying a linear reciprocating motion to a test object,
The linear reciprocating mechanism is
A crankcase,
An inner sun gear fixedly disposed on the crankcase;
A planetary gear member that rotates and revolves while meshing a planetary gear having a pitch circle diameter of half the pitch circle diameter of the inner circumferential sun gear with the inner circumferential sun gear;
A crank member disposed in the crankcase so as to rotate coaxially with a center line of the inner peripheral sun gear, and supporting the planetary gear member so as to be capable of rotating and revolving;
An action portion that is disposed on the planetary gear member on the pitch circle of the planetary gear as viewed from an infinite point in the rotational axis direction of the planetary gear, and linearly reciprocates with the rotation of the crank member;
With
A fatigue testing machine that linearly reciprocates the DUT through the action portion.

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