JP2020197522A - Vibration damper test device - Google Patents

Abstract

To provide a vibration damper test device capable of inputting displacement of an actuator into a vibration damper while amplifying it while keeping an amplification factor input to the vibration damper constant, and performing test satisfactorily by accelerating vibration performance.SOLUTION: A test device 1 includes not rotatable movable first and second movable bodies 3A, 3B and a ball screw mechanism 5 for amplifying relative displacement of the vibration damper 21. The ball screw mechanism 5 includes a first and a second nuts 10A, 10B provided on the first and second movable bodies 3A, 3B, and a rotatable immovable screw shaft 11 having first and second screws 12A, 12B constituting first and second ball screws 13A, 13B therewith. The first and second ball screws 13A and 13B have an inverse screw relationship. A vibration damper 21 is disposed between the first and second movable bodies 3A and 3B. An actuator 4 vibrates the vibration damper 21 via the first movable body 3A.SELECTED DRAWING: Figure 1

Description

The present invention relates to a vibration damping damper test device for testing a vibration damping damper that suppresses vibration by causing the first member and the second member to be displaced relative to each other in the axial direction.

As a conventional vibration damping damper test device, for example, one disclosed in Patent Document 1 is known. This test device is intended for a mass damper, and includes a horizontally extending support frame, an actuator that vibrates the mass damper, and a control device that controls the actuator. The support frame is made by assembling a plurality of frame materials made of steel in a grid shape. The actuator has predetermined vibration performance (maximum load, maximum amplitude and maximum speed) and is arranged on one side in the support frame.

The mass damper is a ball screw type and has an inner cylinder, a screw shaft movable with respect to the inner cylinder, and a rotating mass that rotates with the movement of the screw shaft. The inner cylinder is connected to the other side of the support frame, and the screw shaft is connected to the actuator via a connecting member. Further, this test device is provided with a load cell that detects a load acting on a connecting member as a damper reaction force, and a displacement sensor that detects a relative displacement of a screw shaft with respect to an inner cylinder of a mass damper as a damper displacement.

According to this configuration, when the performance test of the mass damper is performed, the actuator is driven under the control of the control device, the exciting force thereof is input to the mass damper via the connecting member, and the mass damper is operated. Then, the performance of the mass damper is evaluated based on the damper reaction force detected by the load cell, the damper displacement detected by the displacement sensor, and the like.

JP-A-2017-36982

As described above, in the conventional test device, since the actuator is connected in series with one end side of the damper, the excitation performance (maximum load, maximum amplitude and maximum speed) of the actuator remains as it is. become. For this reason, the vibration performance of the test apparatus is limited, and for example, the maximum amplitude and the maximum speed may be insufficient for the desired test conditions.

In such a case, it is conceivable to use an amplification mechanism that amplifies the displacement of the actuator, for example, a pantograph type amplification mechanism. However, since the pantograph type amplification mechanism has a characteristic that it becomes geometrically non-linear, especially when its shape is close to a straight line, even if the output waveform of the actuator is a sine wave, for example, the input waveform to the damper is a sine wave. It does not become a wave and the test cannot be performed well.

The present invention has been made to solve the above problems, and is input to the vibration damping damper while amplifying the displacement due to the vibration of the actuator while keeping the amplification factor input to the vibration damping damper constant. It is an object of the present invention to provide a test device for a vibration damping damper capable of performing a good test by increasing the vibration performance.

In order to achieve this object, the invention according to claim 1 is a vibration damping damper test device for testing a vibration damping damper that suppresses vibration by relatively displaced the first member and the second member in the axial direction. , The immovable first reaction force wall and the second reaction force wall arranged at intervals in the axial direction, and the first movable wall which is non-rotatable and movable in the axial direction, which is arranged at intervals in the axial direction. It is provided with a body and a second movable body and a ball screw mechanism for amplifying a relative displacement between the first and second members of the vibration damping damper, and the ball screw mechanism is provided for the first and second movable bodies, respectively. The first screw and the second nut, which are provided and arranged coaxially with each other, and the first screw and the first screw which mesh with the first and second nuts via balls, respectively, to form the first ball screw and the second ball screw, respectively. It has a second screw, a screw shaft that is rotatably supported by a second reaction force wall and is immovably supported in the axial direction, and the first ball screw and the second ball screw have a reverse screw relationship with each other. Set, the vibration damping damper is placed between the first and second movable bodies, the first and second members are connected to the first and second movable bodies, respectively, and the first reaction force wall and the first movable body. It is characterized by further including an actuator arranged between the bodies and for vibrating the vibration damping damper in the axial direction via the first movable body.

According to this configuration, when the actuator is operated during the test of the vibration damping damper, the first movable body and the first member of the vibration damping damper are displaced (vibrated) in the axial direction by the exciting force. The displacement of the first movable body is converted into the rotational movement of the screw shaft by the first ball screw (first nut and first screw) of the ball screw mechanism, so that the screw shaft rotates. Further, the rotation of the screw shaft is converted into a linear motion of the second movable body by the second ball screw (the second screw and the second nut), so that the second movable body is displaced in the axial direction and is controlled. Drives the second member of the vibration damper.

In this case, according to the present invention, since the first ball screw and the second ball screw have a reverse screw relationship with each other (for example, when one is a right-hand screw and the other is a left-hand screw), the second movable body is first movable. The first member and the second member of the vibration damping damper, which are displaced in the opposite direction to the body and connected to them, are also displaced in the opposite directions to each other. As a result, the relative displacements of the first and second members of the damping damper (hereinafter, appropriately referred to as "relative displacement of the damping damper") are the displacement D1 (absolute value) of the first movable body and the displacement of the second movable body. It is the sum of D2 (absolute value), and the displacement of the actuator is amplified by the displacement D2 of the second movable body.

The ratio (= D2 / D1) of the displacement D2 of the second movable body to the displacement D1 of the first movable body is the ratio of the lead L2 of the second ball screw to the lead L1 of the first ball screw (= L2 /). Equal to L1). From the above, the displacement amplification factor (amplification factor of the relative displacement of the vibration damping damper with respect to the displacement of the actuator) RA is expressed by the following equation (1).
RA = (D1 + D2) / D1 = (L1 + L2) / L1 ... (1)

As described above, according to the test apparatus of the present invention, the amplification factor input to the vibration damping damper is determined by the action of the first and second ball screws of the ball screw mechanism provided between the actuator and the vibration damping damper. While keeping it constant, it can be input to the damping damper while amplifying the displacement due to the vibration of the actuator. As a result, the test can be performed satisfactorily by increasing the vibration performance. Further, the existing actuator can be used as it is without the need to enhance the vibration performance of the actuator itself.

The invention according to claim 2 is characterized in that, in the vibration damping damper test apparatus according to claim 1, the lead of the second ball screw is set to a value larger than that of the lead of the first ball screw. ..

As described above, in the test apparatus of claim 1, the displacement amplification factor RA is represented by the above formula (1), and the larger the displacement D2 of the second movable body is, the larger it is. Further, the displacement D2 of the second movable body becomes larger as the lead L2 of the second ball screw is larger than the lead L1 of the first ball screw. Therefore, according to this configuration, by setting the lead of the second ball screw to a value larger than that of the lead of the first ball screw, a larger displacement amplification factor can be obtained and the excitation performance is further increased. can do.

Further, in order to achieve the above object, the invention according to claim 3 is a vibration damping damper test device for testing a vibration damping damper that suppresses vibration by relative displacement of the first member and the second member in the axial direction. Therefore, the immovable first reaction force wall and the second reaction force wall arranged at intervals in the axial direction, and the non-rotatable and movable in the axial direction, which are arranged at intervals in the axial direction. The ball screw mechanism includes a 1 movable body and a 2nd movable body, and a ball screw mechanism for amplifying a relative displacement between the 1st and 2nd members of the vibration damping damper, and the ball screw mechanism is a 1st and 2nd movable body. The first nut and the second nut, which are provided in the above and are arranged coaxially with each other, and the first and second nuts, respectively, mesh with each other via a ball to form a first ball screw and a second ball screw, respectively. It has a screw and a second screw, and has a screw shaft that is rotatably and immovably supported on a second reaction wall in the axial direction, and the lead of the second ball screw is from the lead of the first ball screw. Is also set to a large value, a reaction force wall for dampers is provided on the side opposite to the first reaction force wall with respect to the second movable body, and the vibration damping damper is placed between the second movable body and the reaction force wall for dampers. The first and second members are connected to the second movable body and the reaction force wall for the damper, respectively, are arranged between the first reaction force wall and the first movable body, and are controlled via the first movable body. It is characterized by further including an actuator for vibrating the vibration damper in the axial direction.

According to this configuration, when the actuator is operated during the test of the vibration damping damper, the first movable body is displaced (vibrated) in the axial direction by the exciting force. The displacement of the first movable body is converted into the rotational movement of the screw shaft by the first ball screw (first nut and first screw) of the ball screw mechanism, so that the screw shaft rotates. Further, the rotation of the screw shaft is converted into a linear motion of the second movable body by the second ball screw (the second screw and the second nut), so that the second movable body is displaced in the axial direction and is controlled. Drives the first member of the vibration damper.

In this case, according to the present invention, since the lead L2 of the second ball screw is larger than the lead L1 of the first ball screw, the displacement D2 of the second movable body is the displacement D1 of the first movable body, that is, the displacement of the actuator. The ratio D2 / D1 is equal to the ratio (= L2 / L1) of the lead L2 of the second ball screw and the lead L1 of the first ball screw. Further, since the second member of the damping damper is connected to the reaction force wall for the damper, the displacement amplification factor (amplification factor of the relative displacement of the damping damper with respect to the displacement of the actuator) RA is equal to the above ratio D2 / D1. .. From the above, the displacement amplification factor RA is represented by the following equation (2).
RA = D2 / D1 = L2 / L1 ... (2)
As is clear from the comparison with the above formula (1), this displacement amplification factor RA is smaller than the displacement amplification factor RA by the test apparatus according to claim 1 under the same lead conditions.

As described above, according to the test apparatus of the present invention, although the displacement amplification factor is lower than that of the test apparatus of claim 1, the first and second balls of the ball screw mechanism are similar to the test apparatus of claim 1. By the action of the screw, it is possible to input to the vibration damping damper while amplifying the displacement due to the vibration of the actuator while keeping the amplification factor input to the vibration damping damper constant. As a result, the test can be performed satisfactorily by increasing the vibration performance. Further, the existing actuator can be used as it is without the need to enhance the vibration performance of the actuator itself.

According to a fourth aspect of the present invention, in the vibration damping damper test device according to any one of claims 1 to 3, the ball screw mechanism is composed of a plurality of ball screw mechanisms provided in parallel with each other. It is a feature.

According to this configuration, since a plurality of ball screw mechanisms parallel to each other are provided as the ball screw mechanism, the reaction force of the vibration damping damper is shared and supported by the plurality of screw shafts of the plurality of ball screw mechanisms. Will be done. Therefore, by appropriately setting the number of ball screw mechanisms, the damping damper reaction force can be supported without excess or deficiency.

The invention according to claim 5 is characterized in that, in the test apparatus for the vibration damping damper according to any one of claims 1 to 4, a buckling prevention mechanism for preventing buckling of the screw shaft is further provided.

According to this configuration, the buckling of the screw shaft, which may occur due to the action of a compressive load during the test, can be effectively prevented by the buckling prevention mechanism.

It is a figure which shows typically the test apparatus according to 1st Embodiment of this invention together with a mass damper. It is a figure which shows the test apparatus of FIG. 1 in different operating states. It is sectional drawing of a mass damper. It is a block diagram which shows the control apparatus of a test apparatus. It is the same figure as FIG. 1 which shows the test apparatus by the 1st modification of 1st Embodiment. It is the same figure as FIG. 1 which shows the test apparatus by the 2nd modification of 1st Embodiment. It is a figure which shows schematicly about the test apparatus according to 2nd Embodiment of this invention together with a mass damper.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 schematically shows a test device 1 according to a first embodiment of the present invention together with a mass damper 21 as a vibration damping damper to be tested. The mass damper 21 is for suppressing vibration of a structure such as a building, and is configured in the same manner as the mass damper described in FIG. 3 of Japanese Patent No. 5314201 by the applicant. First, the configuration and operation of the mass damper 21 will be briefly described.

As shown in FIG. 3, the mass damper 21 has an inner cylinder 22, a ball screw 23, a rotating mass 24, and a limiting mechanism 25. The inner cylinder 22 is made of a cylindrical steel material. One end of the inner cylinder 22 is open, and the other end is attached to the second flange 27 via a universal joint.

Further, the ball screw 23 has a screw shaft 23a and a nut 23c that is rotatably screwed to the screw shaft 23a via a large number of balls 23b. One end of the screw shaft 23a is housed in the opening of the inner cylinder 22 described above, and the other end of the screw shaft 23a is attached to the first flange 26 via a universal joint. Further, the nut 23c is rotatably supported by the inner cylinder 22 via a bearing 28. In FIG. 1, only the main elements of the mass damper 21 are coded.

The rotating mass 24 is made of a material having a large specific gravity, for example, iron, and is formed in a cylindrical shape. Further, the rotating mass 24 is coaxially arranged on the outer peripheral side of the inner cylinder 22 and the ball screw 23, and is rotatably supported by the inner cylinder 22 via a bearing 29. A pair of ring-shaped seals 30 and 30 are provided between the rotating mass 24 and the inner cylinder 22. The space formed by the seals 30, 30, the rotating mass 24, and the inner cylinder 22 is filled with a viscous body 31 composed of silicone oil.

In the mass damper 21 configured as described above, when a relative displacement occurs between the inner cylinder 22 and the screw shaft 23a, the relative displacement is converted into a rotary motion by the ball screw 23, and the relative displacement is converted into a rotational motion by the ball screw 23 via the limiting mechanism 25. The rotary mass 24 rotates by being transmitted to the rotary mass 24. As a result, vibration damping performance that suppresses vibration of structures and the like is exhibited by the rotational inertia mass effect of the rotating mass 24 and the viscous damping effect of the shear resistance of the viscous body 31.

The limiting mechanism 25 is composed of a ring-shaped rotary sliding member 25a, a plurality of screws 25b, and a spring 25c (only two are shown). The rotary mass 24 rotates integrally with the nut 23c until the load acting in the axial direction of the mass damper 21 (hereinafter referred to as “axial load”) reaches a limit load determined according to the degree of tightening of the screw 25b. On the other hand, when the axial load of the mass damper 21 reaches the limit load, slippage occurs between the rotary sliding member 25a and the nut 23c or the rotary mass 24.

Next, the test apparatus 1 will be described with reference to FIG. The test device 1 is for performing a performance test of the mass damper 21 by installing the mass damper 21 and vibrating it under predetermined conditions. As shown in the figure, the test apparatus 1 is an actuator 4 that vibrates the immovable first reaction force wall 2A and second reaction force wall 2B, the first movable frame 3A and the second movable frame 3B, and the mass damper 21. A plurality of ball screw mechanisms 5 for amplifying the displacement of the actuator 4 at the time of vibration and inputting the displacement to the mass damper 21 are provided.

The first and second reaction force walls 2A and 2B are formed by assembling a plurality of steel materials such as H steel, have high rigidity, are integrally erected on the foundation plate 6, and are mutually erected in the left-right direction. They are arranged at intervals. The second reaction force wall 2B on the right side is provided with a plurality of support block portions 7 for supporting the screw shafts 11 of the plurality of ball screw mechanisms 5.

The first and second movable frames 3A and 3B are formed by connecting a plurality of steel plates to each other to form a frame, respectively, and a pair of left and right outer plates 3c and 3c facing each other and upper and lower outer plates 3c and 3c. It has a middle plate 3d connected between the centers in the direction, a bottom plate 3e connected between the lower ends of the outer plates 3c and 3c, and the like. The first and second movable frames 3A and 3B are arranged between the first and second reaction force walls 2A and 2B in order from the first reaction force wall 2A side.

Further, guides 8 are provided on the bottom plates 3e of the first and second movable frames 3A and 3B so as to project downward, and these guides 8 and 8 are provided so as to extend in the left-right direction on the base plate 6. It is engaged with the rail 9. With this configuration, the first and second movable frames 3A and 3B are non-rotatably supported by the rail 9 via the guide 8 and are movably guided along the rail 9 in the left-right direction.

As shown in FIG. 1, the above-mentioned mass damper 21 is installed between the first and second movable frames 3A and 3B at the time of the test. Specifically, the first flange 26 of the mass damper 21 is integrally connected to the center of the outer plate 3c of the first movable frame 3A, and the second flange 27 is integrally connected to the center of the outer plate 3c of the second movable frame 3B. Will be done.

The actuator 4 is, for example, a dynamic actuator composed of a hydraulic cylinder that performs double-acting linear motion, and has predetermined vibration performance, for example, maximum load: ± 3000 kN, maximum amplitude: ± 100 mm, maximum speed: ± 300 mm / s. Has the performance of.

The actuator 4 has a cylinder 4a and a piston portion 4b that can be expanded and contracted with respect to the cylinder 4a. The piston portion 4b is composed of a piston rod and a piston head that are integrally connected to a piston (not shown) sliding in the cylinder 4a in this order. The actuator 4 is arranged between the first reaction force wall 2A and the first movable frame 3A. Specifically, the cylinder 4a is integrally connected to the first reaction force wall 2A, and the piston head of the piston portion 4b. Is integrally connected to the center of the outer plate 3c of the first movable frame 3A.

With the above configuration, the actuator 4 vibrates the mass damper 21 in the axial direction via the first movable frame 3A by reciprocating the piston portion 4b in the left-right direction during operation.

As shown in FIG. 1, each of the plurality of ball screw mechanisms 5 (only two are shown) has a first nut 10A, a second nut 10B, and a screw shaft 11. The first nut 10A is fixed between the outer plates 3c and 3c of the first movable frame 3A. The second nut 10B is fixed between the outer plates 3c and 3c of the second movable frame 3B and is arranged coaxially with the first nut 10A.

The screw shaft 11 has a first screw 12A on the left side portion of FIG. 1 and a second screw 12B on the right side portion. The first screw 12A meshes with the first nut 10A via a ball (not shown), and the first nut 10A, the ball, and the first screw 12A constitute the first ball screw 13A. The second screw 12B meshes with the second nut 10B via a ball (not shown), and the second nut 10B, the ball, and the second screw 12B constitute the second ball screw 13B.

The first ball screw 13A and the second ball screw 13B are in a reverse screw relationship with each other. In the example of FIG. 1, the first ball screw 13A is set to the right-hand screw and the second ball screw 13B is set to the left-hand screw. ing. Further, the lead L2 of the second ball screw 13B is larger than the lead L1 of the first ball screw 13A, and is set to, for example, L1 = 25 mm and L2 = 60 mm.

The screw shaft 11 extends to both the left and right sides of the first and second movable frames 3A and 3B, and at the right end portion, the screw shaft 11 is connected to the support block portion 7 of the second reaction force wall 2B via the radial bearing 14 and the thrust bearing 15. It is supported so that it can rotate and cannot move in the axial direction. Further, the portion of the screw shaft 11 between the first screw 12A and the second screw 12B has a larger cross section than the first and second screws 12A and 12B in order to prevent the screw shaft 11 from buckling. It is part 16.

The test device 1 further includes a load cell 17 and a displacement sensor 18 (see FIG. 4). The load cell 17 is provided at the tip of the actuator 4, and detects a load acting on the mass damper 21 from the actuator 4 via the first movable frame 3A as a reaction force (hereinafter referred to as “damper reaction force”) PMD of the mass damper 21. The detection signal is output to the control device 20.

The displacement sensor 18 detects the displacement (hereinafter referred to as “damper displacement”) DMD of the screw shaft 23a with respect to the inner cylinder 22 of the mass damper 21, and outputs the detection signal to the control device 20. The control device 20 is composed of a combination of a power supply for driving the actuator 4, a CPU, RAM, ROM, an I / O interface, and the like.

In the test device 1 having the above configuration, the mass damper 21 which is a test body is set between the first and second movable frames 3A and 3B as described above, and the actuator 4 is operated under the control of the control device 20. The test is performed by vibrating the mass damper 21 under the conditions of a predetermined waveform (sine wave or seismic response wave) and magnitude. Then, the maximum velocity resistance, damping coefficient, rotational inertia mass, etc. of the mass damper 21 are calculated according to the damper reaction force PMD and the damper displacement DMD detected by the load cell 17 and the displacement sensor 18 during the test, and the performance of the mass damper 21 is calculated. Is evaluated.

Next, the mechanical operation of the test device 1 in response to the vibration of the actuator 4 during this test will be described in detail with reference to FIGS. 1 and 2. Note that FIG. 1 shows a state in which the piston portion 4b of the actuator 4 is located on the leftmost side, and the screw shaft 23a of the first movable frame 3A and the mass damper 21 is also located on the leftmost side.

When the actuator 4 operates and the piston portion 4b moves to the right from the position shown in FIG. 1, the screw shafts 23a of the first movable frame 3A and the mass damper 21 are displaced by the same amount as the piston portion 4b by the guidance of the guide 8 and the rail 9. , Displace (move) to the right (arrow X1 in FIG. 1). The displacement of the first movable frame 3A is converted into the rotational movement of the screw shaft 11 by the first ball screw 13A (the first nut 10A and the first screw 12A) in each of the plurality of ball screw mechanisms 5. The screw shaft 11 rotates. Further, the rotation of the screw shaft 11 is converted into a linear motion of the second movable frame 3B by the second ball screw 13B (the second screw 12B and the second nut 10B), whereby the second movable frame 3B is converted into a linear motion. It is displaced by the guidance of the guide 8 and the rail 9, and drives the inner cylinder 22 of the mass damper 21.

In this case, in the present embodiment, since the first ball screw 13A and the second ball screw 13B have a reverse screw relationship with each other, the second movable frame 3B is always displaced in the opposite direction to the first movable frame 3A. The screw shaft 23a and the inner cylinder 22 of the mass damper 21 connected to them are also displaced in opposite directions. For example, in the situation of FIG. 1, the first movable frame 3A and the screw shaft 23a are displaced to the right (arrow X1), whereas the second movable frame 3B and the inner cylinder 22 are displaced to the left (arrow X2). .. As a result, the relative displacement between the inner cylinder 22 of the mass damper 21 and the screw shaft 23a is the sum of the displacement D1 (absolute value) of the first movable frame 3A and the displacement D2 (absolute value) of the second movable frame 3B. The displacement of the actuator 4 is amplified by the displacement D2 of the latter 3B.

Further, in the present embodiment, since the lead L2 of the second ball screw 13B is set to a value larger than the lead L1 of the first ball screw 13A, the inner cylinder 22 and the screw shaft of the mass damper 21 with respect to the displacement of the actuator 4 The amplification factor (hereinafter referred to as “displacement amplification factor”) RA of the relative displacement with respect to 23a becomes larger. This point will be described below.

As described above, assuming that the lead L1 of the first ball screw 13A is 25 mm and the lead L2 of the second ball screw 13B is 60 mm, and the actuator 4 is displaced to the right by 25 mm, which is equal to the lead L1, for example, the screw shaft 23a While displaced by the same amount (= 25 mm), the screw shaft 11 makes one rotation due to the action of the first ball screw 13A, and accordingly, the action of the second ball screw 13B causes the lead L2 to be 60 mm and the second movable. The frame 3B and the inner cylinder 22 are displaced to the left. Therefore, the displacement amplification factor RA at this time is RA = (L1 + L2) / L1 = (25 + 60) / 25 = 3.4, and a very large amplification factor can be obtained.

Therefore, the maximum load input to the mass damper 21 is ± 3000 / 3.4 = with respect to the vibration performance (maximum load: ± 3000 kN, maximum amplitude: ± 100 mm, maximum speed: ± 300 mm / s) of the actuator 4 described above. Although it decreases to about 882 kN, the maximum amplitude and maximum velocity can be amplified to ± 340 mm and ± 1020 mm / s, which are 3.4 times, respectively.

As described above, according to the test apparatus 1 of the present embodiment, the actuator 4 is added by the action of the first and second ball screws 13A and 13B of the ball screw mechanism 5 provided between the actuator 4 and the mass damper 21. It can be input to the mass damper 21 while amplifying the displacement due to the vibration. In this case, by setting the lead L2 of the second ball screw 13B to a value larger than the lead L1 of the first ball screw 13A, a larger displacement amplification factor RA can be obtained.

As described above, while maintaining the amplification factor input to the damping damper at a constant level, the displacement due to the vibration of the actuator 4 can be amplified and input to the mass damper 21. As a result, the test can be performed by increasing the vibration performance. It can be done well. Further, the existing actuator can be used as it is without the need to enhance the vibration performance of the actuator 4 itself.

Further, as the ball screw mechanism 5, a plurality of ball screw mechanisms 5 parallel to each other are provided, and the reaction force of the mass damper 21 and the like are shared and supported by the plurality of screw shafts 11 of the plurality of ball screw mechanisms 5. To. Therefore, by appropriately setting the number of the ball screw mechanisms 5, the reaction force of the mass damper 21 can be supported without excess or deficiency.

Further, the buckling prevention portion 16 provided on each screw shaft 11 can effectively prevent the buckling of the screw shaft that may occur due to the action of a compressive load during the test. Further, the guides 8 and rails 9 provided on the bottom plates 3e of the first and second movable frames 3A and 3B non-rotatably support the first and second movable actuators 3A and 3B, and smoothly guide them in the axial direction. can do.

Next, the test apparatus 41 according to the first modification of the first embodiment will be described with reference to FIG. Compared with the test device 1 of the first embodiment of FIG. 1, this test device 41 is provided between the first and second screws 12A and 12B of the screw shaft 11 of each ball screw mechanism 5 to prevent buckling. The main difference is that the portion 16 is omitted and this portion of the screw shaft 11 is supported by the central reaction force wall 2C.

The central reaction force wall 2C is formed by assembling a plurality of steel materials such as H steel together with braces, and has high rigidity. On the other hand, the portion between the first and second screws 12A and 12B of the screw shaft 11 of each ball screw mechanism 5 is a smooth portion 11a having substantially the same diameter as the other portions and having no screw on the surface. Each screw shaft 11 is rotatably and non-movably supported by the reaction force wall 2C in the smooth portion 11a via the radial bearing 42 and the thrust bearing 43. Other configurations are the same as in the first embodiment.

According to this test device 41, one end of the screw shaft 11 of each ball screw mechanism 5 is supported by the second reaction force wall 2B via the radial bearing 14 and the thrust bearing 15, and the screw shaft The smooth portion 11a at the center of 11 is supported by the reaction force wall 2C via the radial bearing 42 and the thrust bearing 43. As a result, the screw shaft 11 can be supported stably and smoothly because it is rotatable and immovable in the axial direction. The thrust bearing 43 of the reaction force wall 2C may be omitted.

Further, by passing the central portion of the screw shaft 11 between the radial bearings 42 and 42 of the reaction force wall 2C, buckling of the screw shaft 11 can be effectively prevented. That is, the reaction force wall 2C also functions as a buckling prevention mechanism. Further, the buckling prevention portion 16 of the first embodiment has a large cross-sectional area, and when it rotates together with the screw shaft 11, a large rotational moment of inertia is generated, whereas in this test device 41, such a problem occurs. Can be avoided.

Next, the test apparatus 51 according to the second modification of the first embodiment will be described with reference to FIG. Compared with the test device 41 of the first modification described above, the test device 51 omits the support block portion 7, the radial bearing 14, and the thrust bearing 15 provided on the second reaction force wall 2B. different.

Specifically, each screw shaft 11 of the ball screw mechanism 5 is rotatable and axially axial to the reaction force wall 2C via the radial bearing 42 and the thrust bearing 43 at the central portion thereof, as in the first modification. It is supported by immobility. Further, the right end side of the screw shaft 11 extends to the vicinity of the second reaction force wall 2B and is in a free state. Further, the first reaction force wall 2A, the second reaction force wall 2B excluding the support block portion 7, the foundation plate 6, and the upper plate 52 are connected to each other to form a support frame, and the reaction force wall 2C Is fixed to the base plate 6 and the upper plate 52.

According to the test device 51 having the above configuration, the same operation as that of the test device 41 of the first modification can be obtained. Further, since the radial bearing 14 and the thrust bearing 15 are omitted, the number of parts and the manufacturing cost can be reduced.

Next, the test apparatus 61 according to the second embodiment of the present invention will be described with reference to FIG. 7. In this test device 61, the mass damper 21 is arranged between the second movable frame 3B and the reaction force wall 62 for the damper as compared with the first embodiment, so that a displacement amplification factor RA different from that of the first embodiment is obtained. The points are mainly different.

Specifically, the second reaction force wall 2B is arranged between the first and second movable frames 3A and 3B, and is erected on the foundation plate 6. The screw shaft 11 of each ball screw mechanism 5 is passed through the second reaction force wall 2B, and at the central portion between the first and second screws 12A and 12B, via the radial bearing 14 and the thrust bearing 15, It is supported by the second reaction force wall 2B so as to be rotatable and immovable in the axial direction.

The reaction force wall 62 for the damper is on the opposite side of the first reaction force wall 2A with respect to the second movable frame 3B, and in the example of FIG. 7, on the right end side opposite to the first reaction force wall 2A located on the left end side. Have been placed. Like other reaction force walls, the damper reaction force wall 62 is formed by assembling a plurality of steel materials such as H steel, has high rigidity, and is integrally erected on the foundation plate 6. ..

The mass damper 21 is installed between the second movable frame 3B and the damper reaction force wall 62. Specifically, the first flange 26 of the mass damper 21 is integrally connected to the center of the outer plate 3c of the second movable frame 3B, and the second flange 27 is integrally connected to the center of the reaction force wall 62 for the damper in the vertical direction. Will be done.

The first ball screw 13A and the second ball screw 13B may be in a reverse screw relationship or a forward screw relationship with each other for the reason described later. In the example of FIG. 7, the first and second ball screws 13A and 13B are Due to the forward screw, both are set to right-handed. Further, as in the test apparatus 1 of the first embodiment, the lead L2 of the second ball screw 13B is larger than the lead L1 of the first ball screw 13A, and is set to L1 = 25 mm and L2 = 60 mm. Other configurations are the same as in the first embodiment.

During the test by the test device 61, when the actuator 4 operates and the piston portion 4b moves to the right from the position shown in FIG. 7, the first movable frame 3A is displaced to the right by the same amount (arrow in FIG. 7). Y1). The displacement of the first movable frame 3A is converted into the rotational motion of the screw shaft 11 by the first ball screw 13A of each ball screw mechanism 5, and the rotation of the screw shaft 11 is converted into the second by the second ball screw 13B. By being converted into the linear motion of the movable frame 3B, the second movable frame 3B is displaced and drives the screw shaft 23a of the mass damper 21.

In this case, in the present embodiment, since the first ball screw 13A and the second ball screw 13B are in a forward screw relationship with each other, the second movable frame 3B is always displaced in the same direction as the first movable frame 3A. In the example of FIG. 7, it is displaced to the right (arrow Y2). Further, as described above, since the lead L1 of the first ball screw 13A is 25 mm and the lead L2 of the second ball screw 13B is 60 mm, when the actuator 4 is displaced to the right by 25 mm, which is equal to the lead L1, for example, each The screw shaft 11a makes one rotation, and accordingly, the second movable frame 3B, which is 60 mm equal to the lead L2, is displaced to the right to drive the screw shaft 23a of the mass damper 21. The inner cylinder 22 of the mass damper 21 is fixed to the reaction force wall 62 for the damper.

Therefore, the displacement amplification factor RA at this time is RA = L2 / L1 = 60/25 = 2.4, and although a large amplification factor can be obtained, the displacement amplification factor according to the first embodiment under the same lead conditions. It is smaller than RA (= 3.4).

As described above, according to the test apparatus 61 of the present embodiment, although the displacement amplification factor RA is lower than that of the first embodiment, the actuator 4 of the actuator 4 keeps the amplification factor input to the mass damper 21 constant. The effects of the first embodiment described above can be similarly obtained, for example, the displacement due to vibration can be amplified and input to the mass damper 21, and the test can be performed satisfactorily by increasing the vibration performance.

In the second embodiment, the first and second ball screws 13A and 13B are set to have a forward screw relationship, but may be set to a reverse screw relationship. In that case, the only difference is that the second movable frame 3B is displaced in the direction opposite to that of the first movable frame 3A, and the same effect as described above can be obtained.

Further, the present invention is not limited to the described embodiments and modifications, and can be carried out in various embodiments. For example, in the embodiment, the actuator 4 is composed of a hydraulic cylinder, but may be any as long as it vibrates the vibration damping damper and relatively displaces the first and second members thereof, for example, it is composed of an electric motor. You may. Further, in the embodiment, the mass damper 21 is used as the vibration damping damper to be tested, but it may be any one that exerts the vibration damping effect by the relative displacement of the first and second members, for example, an oil damper or a viscoelastic damper. , Viscoelastic dampers, steel dampers, and friction dampers can be used.

Further, in the embodiment, the number of ball screw mechanisms 5 to be installed is not limited, but it is preferable to increase or decrease the number as appropriate according to the assumed reaction force of the vibration damping damper. Further, in the embodiment, the first and second movable bodies provided with the first and second nuts are formed of a movable frame, but it is needless to say that a shape other than the frame may be used. .. In addition, it is possible to appropriately change the detailed configuration within the scope of the gist of the present invention.

1 Test device according to the first embodiment 2A 1st reaction force wall 2B 2nd reaction force wall 2C Reaction force wall (buckling prevention mechanism)
3A 1st movable frame (1st movable body)
3B 2nd movable frame (2nd movable body)
4 Actuator 5 Ball screw mechanism 10A 1st nut 10B 2nd nut 11 Screw shaft 12A 1st screw 12B 2nd screw 13A 1st ball screw 13B 2nd ball screw 16 Anti-swing part (anti-swing mechanism)
21 Mass damper (vibration damping damper)
22 Inner cylinder of mass damper (second member)
23a Mass damper screw shaft (first member)
41 Test device according to the first modification 51 Test device according to the second modification 61 Test device according to the second embodiment 62 Reaction force wall for damper (adjustment member)
L1 1st ball screw lead L2 2nd ball screw lead

Claims (5)

This is a vibration damping damper test device that tests a vibration damping damper that suppresses vibration by causing the first member and the second member to be displaced relative to each other in the axial direction.
Immovable first reaction force wall and second reaction force wall arranged at intervals in the axial direction, and
A first movable body and a second movable body which are arranged at intervals in the axial direction and are non-rotatable and movable in the axial direction.
A ball screw mechanism for amplifying the relative displacement between the first and second members of the vibration damping damper is provided.
The ball screw mechanism is provided on the first and second movable bodies, respectively, and meshes with the first nut and the second nut, which are arranged coaxially with each other, with the first and second nuts via balls, respectively. It has a first screw and a second screw that constitute a 1-ball screw and a second ball screw, respectively, and has a screw shaft that is rotatably supported by the second reaction force wall and is immovably supported in the axial direction. ,
The first ball screw and the second ball screw are set to have a reverse screw relationship with each other.
The vibration damping damper is arranged between the first and second movable bodies, and the first and second members are connected to the first and second movable bodies, respectively.
A control device which is arranged between the first reaction force wall and the first movable body and further includes an actuator for vibrating the vibration damping damper in the axial direction via the first movable body. Vibration damper test equipment. The test device for a vibration damping damper according to claim 1, wherein the lead of the second ball screw is set to a value larger than that of the lead of the first ball screw. This is a vibration damping damper test device that tests a vibration damping damper that suppresses vibration by causing the first member and the second member to be displaced relative to each other in the axial direction.
Immovable first reaction force wall and second reaction force wall arranged at intervals in the axial direction, and
A first movable body and a second movable body which are arranged at intervals in the axial direction and are non-rotatable and movable in the axial direction.
A ball screw mechanism for amplifying the relative displacement between the first and second members of the vibration damping damper is provided.
The ball screw mechanism is provided on the first and second movable bodies, respectively, and meshes with the first nut and the second nut, which are arranged coaxially with each other, with the first and second nuts via balls, respectively. It has a first screw and a second screw that constitute a 1-ball screw and a second ball screw, respectively, and has a screw shaft that is rotatably supported by the second reaction force wall and is immovably supported in the axial direction. ,
The lead of the second ball screw is set to a value larger than that of the lead of the first ball screw.
A damper reaction force wall is provided on the side opposite to the first reaction force wall with respect to the second movable body.
The vibration damping damper is arranged between the second movable body and the reaction force wall for the damper, and the first and second members are connected to the second movable body and the reaction force wall for the damper, respectively.
A control device which is arranged between the first reaction force wall and the first movable body and further includes an actuator for vibrating the vibration damping damper in the axial direction via the first movable body. Vibration damper test equipment. The vibration damping damper test device according to any one of claims 1 to 3, wherein the ball screw mechanism is composed of a plurality of ball screw mechanisms provided in parallel with each other. The vibration damping damper test apparatus according to any one of claims 1 to 4, further comprising a buckling prevention mechanism for preventing buckling of the screw shaft.

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