JP6466281B2 - Mass damper testing equipment - Google Patents

Description

  The present invention relates to a mass damper testing apparatus for testing a limiting mechanism for limiting an axial load, which is a load acting in the axial direction of a cylindrical portion and a screw shaft, in a mass damper having a cylindrical portion, a screw shaft, a nut, and a rotating mass. .

  Conventionally, as this type of mass damper test apparatus, for example, one disclosed in Patent Document 1 is known. The mass damper is engaged with the outer cylinder, a screw shaft partially accommodated in the outer cylinder so as to be movable in the axial direction, and screwed to the screw shaft via a large number of balls, and the screw shaft moves with respect to the outer cylinder. As a result, a nut that rotates with respect to the outer cylinder and the screw shaft, a rotating mass that is rotatable in the outer cylinder and immovable in the axial direction, and a load that acts on the outer cylinder and the screw shaft in the axial direction. It has a limiting mechanism for limiting a certain axial load.

  The limiting mechanism includes a friction plate that contacts the nut and the rotating mass, a coil spring that urges the rotating mass toward the nut, and the like. The biasing force of the coil spring is set to such a magnitude that no slip occurs between the friction plate and the rotating mass or nut until the axial load reaches a predetermined limit load. Thereby, until the axial load reaches the limit load, the rotating mass and the nut rotate together with the relative movement between the outer cylinder and the screw shaft. "Rotational mass reaction force torque" is transmitted to the screw shaft through the nut, and acts to suppress the movement of the screw shaft. The degree of suppression increases as the rotational mass reaction force torque increases, and as a result, the axial load increases. In addition, when the axial load reaches the limit load, slippage occurs between the friction plate and the rotary mass or nut, thereby limiting the transmission of the rotary mass reaction force torque to the screw shaft. Limited to the limit load or less.

  In the above-described conventional test apparatus, through holes and holes communicating with each other in the radial direction are formed in the outer cylinder and the rotary mass of the mass damper, respectively, and rotation is performed by inserting pins into these through holes and holes. The mass is non-rotatably held by the outer cylinder. In this state, by applying an axial load to the screw shaft, the screw shaft is forcibly moved with respect to the outer cylinder, and the axial load at that time is detected as a limit load.

JP2013-167549A

  As described above, in this conventional test apparatus, in order to hold the rotating mass in the outer cylinder so as not to rotate, through holes and holes must be formed in the outer cylinder and the rotating mass, respectively. Further, these through holes and holes must be aligned so as to communicate with each other, and in that state, the pins must be inserted into the through holes and holes. From the above, in the conventional test apparatus, the work required for the test of the limiting mechanism is very complicated, and the test cannot be easily performed.

  The present invention has been made to solve the above-described problems, and an object of the present invention is to provide a mass damper test apparatus that can easily perform a test of a limiting mechanism.

  In order to achieve the above-mentioned object, the invention according to claim 1 is threadedly engaged with a cylindrical portion, a screw shaft partially accommodated in the cylindrical portion so as to be movable in the axial direction, and a screw shaft via a ball. In addition, as the tube portion and the screw shaft move relative to each other, a nut that rotates with respect to the screw shaft and the tube portion, a rotation mass that can be rotated while covering the nut, and an axis line to the tube portion and the screw shaft In order to limit the axial load, which is a load acting in the direction, until the axial load reaches a predetermined limit load, the nut and the rotating mass are connected together via a sliding member to rotate together, and the axial load is A mass damper having a limit mechanism that allows rotation of the rotary mass relative to the nut by sliding one of the nut and the rotary mass with respect to the sliding member when the limit load is reached. Test equipment A fixing means for fixing the cylinder portion and the screw shaft to be unrotatable and unmovable, a rotation drive means for forcibly rotating the rotation mass, and a rotation mass torque parameter representing torque acting on the rotation mass are detected. Based on the rotational mass torque parameter detected when the rotational mass is rotated by the rotational drive means in a state in which the cylindrical portion and the screw shaft are fixed so as not to be rotatable and immovable by the rotational means. And calculating means for calculating a limit load.

  According to this configuration, in the mass damper, as the tube portion and the screw shaft move relative to each other, the nut that is screwed to the screw shaft via the ball rotates with respect to the screw shaft and the tube portion. Further, the rotating mass covers the nut, and the limiting mechanism limits the axial load that is a load acting in the axial direction on the cylindrical portion and the screw shaft. In this case, until the axial load reaches a predetermined limit load, the nut and the rotating mass are connected to each other via the sliding member to rotate integrally. At this time, as is clear from the relationship between the screw shaft and the nut described above, torque due to the reaction force of the rotating mass (hereinafter referred to as “rotating mass reaction force torque”) is transmitted to the screw shaft via the nut, Acts to suppress movement. The degree of suppression increases as the rotational mass reaction force torque increases, and as a result, the axial load increases. In addition, when the axial load reaches the limit load, the rotation of the rotary mass with respect to the nut is allowed by sliding the nut or the rotary mass with respect to the sliding member, whereby the rotary mass reaction force torque on the screw shaft is allowed. By restricting the transmission of the shaft load, the shaft load is limited to the limit load or less.

  Furthermore, in the test apparatus according to the present invention, the cylindrical portion and the screw shaft are fixed so as not to be rotatable and immovable by the fixing means, and the rotating mass is forcibly rotated by the rotation driving means. Further, a rotation mass torque parameter representing torque acting on the rotation mass is detected by the rotation mass torque parameter detecting means. Further, the limit load is calculated by the calculation means based on the rotation mass torque parameter detected when the rotation mass is forcibly rotated while the cylinder portion and the screw shaft are fixed.

  As described above, the axial load increases as the rotational mass reaction force torque increases. In the limiting mechanism, the axial load of the screw shaft or the like is limited to the limit load or less by limiting the transmission of the rotational mass reaction force torque to the screw shaft by sliding the nut or the rotating mass with respect to the sliding member. Is done. As is clear from the above, the rotational mass torque parameter used for the calculation of the above limit load represents the torque of the rotary mass when the axial load reaches the limit load and has a close correlation with the limit load. The load can be calculated with high accuracy. In addition, unlike the above-described conventional test apparatus, instead of moving the screw shaft in a state in which the rotation mass is held non-rotatable in the outer cylinder, the rotation mass is rotated in a state where the cylinder portion and the screw shaft are fixed. The through holes, holes and pins of the conventional test apparatus are not necessary, and therefore the restriction mechanism can be easily tested. Moreover, since the rotation mass has covered the nut and is provided in the outer side, a rotation mass can be rotated easily.

  According to a second aspect of the present invention, in the mass damper testing apparatus according to the first aspect, the rotation driving means includes a sling wound around the rotating mass and a winding wound around the rotating mass in order to forcibly rotate the rotating mass. Tension means for pulling the rotated sling.

  According to this configuration, by pulling the sling wound around the rotating mass with the pulling means, the rotating mass can be rotated more easily, and further, the limiting mechanism can be tested more easily.

It is a top view which shows roughly the flame | frame of the test apparatus by embodiment of this invention with the mass damper to which this is applied. FIG. 3 is a rear view partially showing the test apparatus and mass damper of FIG. 1 with the sling of the test apparatus being wound around the mass damper, (a) when wound clockwise, and (b) when wound counterclockwise. is there. It is a block diagram which shows the load cell and calculation apparatus of the test apparatus of FIG. FIGS. 3A and 3B show transitions of the sling load detected by the load cell of FIG. 3 with the passage of time (a) when the rotating mass is rotated clockwise and (b) when it is rotated counterclockwise. It is. It is sectional drawing of the mass damper of FIG.

  Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the drawings. 1 and 2 schematically show a test apparatus 1 according to the present embodiment together with a mass damper 21 to which the test apparatus 1 is applied. 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 FIGS. 1, 2, and 5, the mass damper 21 includes 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 first flange 26 via a universal joint. The universal joint has a frictional force such that the inner cylinder 22 does not rotate with respect to the first flange 26 due to torque (hereinafter referred to as “rotational mass reaction force torque”) due to the reaction force of the rotation mass 24.

  The ball screw 23 includes a screw shaft 23a and a nut 23c that is rotatably engaged with the screw shaft 23a via a large number of balls 23b. One end of the screw shaft 23a is accommodated in the opening of the inner cylinder 22 described above, and the other end of the screw shaft 23a is attached to the second flange 27 via a universal joint. The universal joint has a frictional force such that the screw shaft 23 a does not rotate with respect to the second flange 27 due to the rotational mass reaction torque (torque due to the reaction force of the rotational mass 24). The nut 23c is supported by the inner cylinder 22 via the bearing 28 so as to be rotatable and immovable in the axial direction.

  The rotary mass 24 is made of a material having a large specific gravity, for example, iron, and is formed in a cylindrical shape. The rotating mass 24 covers the inner cylinder 22 and the nut 23c, and is supported by the inner cylinder 22 via a bearing 29 so as to be rotatable and immovable in the axial direction. A pair of ring-shaped seals 30 and 30 are provided between the rotary mass 24 and the inner cylinder 22. A space formed by the seals 30, 30, the rotation mass 24 and the inner cylinder 22 is filled with a viscous body 31 made of silicon oil.

  In the mass damper 21 configured as described above, when a relative displacement is generated between the inner cylinder 22 and the screw shaft 23 a, the relative displacement is converted into a rotational motion by the ball screw 23, via the limiting mechanism 25. The rotation mass 24 is transmitted to the rotation mass 24, thereby rotating the rotation mass 24.

  The limiting mechanism 25 is for limiting a load acting in the axial direction of the inner cylinder 22 and the screw shaft 23a (hereinafter referred to as “axial load”), and is a ring-shaped member disposed between the nut 23c and the rotary mass. The rotary sliding member 25a is composed of a plurality of screws 25b and springs 25c. In FIG. 1, only four screws 25b are shown, and for convenience, only one symbol of the screw 25b is attached. In FIG. 5, only two screws 25b and springs 25c are shown. The same number of spring accommodating holes as the screws 25b and the springs 25c are formed in the portion of the rotary mass 24 where the rotary sliding material 25a is disposed. These spring accommodation holes are arranged at equal intervals in the circumferential direction and penetrate in the radial direction. A screw 25b is screwed into each spring accommodation hole, and a spring is interposed between the screw 25b and the rotary sliding member 25a. 25c is accommodated.

  With the above configuration, when the screw 25b is strongly tightened, the rotating sliding member 25a is strongly pressed against the nut 23c by the urging force of the spring 25c, so that the rotating mass 24 is integrally connected to the nut 23c via the rotating sliding member 25a. It will be in the state. When the screw 25b is loosened from this state, the tightening degree is lowered, and the above-described axial load (the load acting in the axial direction of the inner cylinder 22 and the screw shaft 23a) is determined according to the tightening degree of the screw 25b. The rotating mass 24 rotates integrally with the nut 23c until the limit load is reached. At this time, as is apparent from the relationship between the screw shaft 23a and the nut 23c described above, the rotational mass reaction force torque is transmitted to the screw shaft 23a via the nut 23c, and acts to suppress the movement of the screw shaft 23a. The degree of suppression increases as the rotational mass reaction force torque increases, and as a result, the axial load increases.

  On the other hand, when the axial load reaches the limit load, slip occurs between the rotary sliding member 25a and the nut 23c or the rotary mass 24, and the rotation of the rotary mass 24 with respect to the nut 23c is allowed. As a result, the transmission of the rotational mass reaction force torque to the screw shaft 23a is restricted, so that the shaft load is restricted to a limit load or less.

  Next, the test apparatus 1 will be described with reference to FIGS. In the following description, for convenience, the upper side and the lower side in FIG. 1 are referred to as “front” and “rear”, respectively, and the left side and the right side are referred to as “left” and “right”, respectively. In the test apparatus 1, by testing the limiting mechanism 25 described above, as the limiting load, the compression-side limiting load RLMP that is the limiting load of the axial load that acts in the direction in which the mass damper 21 contracts, and the mass damper 21 in the extending direction. The tension side limit load RLMS, which is the limit load of the axial load to be calculated, is calculated. In the calculation, the inner cylinder 22 and the screw shaft 23a are fixed, and the rotating mass 24 is forcibly rotated in this state.

  As shown in FIGS. 1 to 3, the test apparatus 1 includes front, rear, left and right frames 2, 3, 4, 5, which are integrally provided in a cross beam shape, and a sling 6 wound around a rotary mass 24 of a mass damper 21. , A hoist 7 for winding up the sling 6, a load cell 11, and a calculation device 12 for calculating the compression side limit load RLMP and the tension side limit load RLMS. FIG. 1 shows the test apparatus 1 and the like when the sling 6 is not wound around the rotary mass 24. Each of the frames 2 to 5 is made of steel, and the front and rear frames 2 and 3 extend in the left-right direction with a space between each other in the front-rear direction. The frames 4 and 5 are connected to each other. The left and right frames 4 and 5 are fixed to a foundation F of a building (not shown) in which the test apparatus 1 is housed, and extend in the front-rear direction with a space in the left-right direction. The first flange 26 of the mass damper 21 is fixed to the front frame 2, and the second flange 27 is fixed to the rear frame 3, whereby the inner cylinder 22 and the screw shaft 23 a are not rotatable and immovable.

  The sling 6 is, for example, a nylon rope and extends in the vertical direction. One end of the sling 6 is connected to the hoist 7 and the other end is connected to a bolt B screwed into the rotary mass 24. . This bolt B is screwed into the rotating mass 24 only when testing the limiting mechanism 25. Note that a steel or synthetic resin cable, a chain, or the like may be used as the sling 6.

  As is apparent from the configuration of the mass damper 21 described above, when an axial load acts in a direction in which the mass damper 21 contracts and the axial load does not reach the compression side limit load RLMP, the nut is viewed from the second flange 27 side. 23c and the rotating mass 24 rotate counterclockwise, and when reaching RLMP, the rotating mass 24 rotates clockwise with respect to the nut 23c. For this reason, when calculating the compression side limit load RLMP, the sling 6 is forced to rotate clockwise as viewed from the second flange 27 side, as shown in FIG. Then, it is wound around the rotary mass 24 clockwise from the other end toward the hoist 7 side. The sling 6 is wound by an operator.

  On the other hand, when an axial load acts in the direction in which the mass damper 21 extends and the axial load does not reach the tensile limit load RLMS, the nut 23c and the rotary mass 24 rotate clockwise as viewed from the second flange 27 side. When the RLMS is reached, the rotary mass 24 rotates counterclockwise with respect to the nut 23c. For this reason, when calculating the tension side limit load RLMS, the sling 6 is rotated as shown in FIG. 2B in order to forcibly rotate the rotary mass 24 counterclockwise as viewed from the second flange 27 side. In addition, it is wound around the rotary mass 24 counterclockwise from the other end toward the hoist 7 side. The operator also performs the winding of the sling 6.

  The sling 6 may be wound directly around the rotary mass 24 or may be wound via a sheet (not shown) for protecting the surface of the rotary mass 24. In particular, when a steel chain or the like is used as a sling, the surface of the rotating mass is likely to be damaged if such a sling is directly wound around the rotating mass. Is preferred.

  Moreover, the hoist 7 is comprised by the combination of an electric motor, a pulley, etc., is attached to the ceiling C of the said building, and pulls up the sling 6 by operating by an operator. The hoist 7 may be attached to the foundation F. The load cell 11 is of a strain gauge type, for example, and is provided between the sling 6 and the hoist 7 (omitted for convenience in FIG. 2), and a load acting on the sling 6 (hereinafter referred to as “sling load”) FSL While detecting, the detection signal is output to the calculation device 12. The load cell 11 may be a capacitance type or other appropriate type. The calculation device 12 is composed of a combination of a CPU, RAM, ROM, I / O interface, and the like.

  In the test apparatus 1 having the above configuration, the restriction mechanism 25 is tested as follows. That is, the sling 6 wound around the rotary mass 24 by the operator as described above is wound up by the hoist 7 while the inner cylinder 22 and the screw shaft 23a are fixed to the frames 2 to 5 so as not to rotate and move. Thereby, the rotation mass 24 is forcibly rotated clockwise when calculating the compression-side limit load RLMP and counterclockwise when calculating the tension-side limit load RLMS. FIG. 4A shows an example of the transition of the sling load FSL with the passage of time (t) from the start of winding of the sling 6 by the hoist 7 for rotating the rotary mass 24 clockwise. FIG. 4B shows an example of the transition of the sling load FSL with the passage of time (t) from the start of winding of the sling 6 for rotating the rotary mass 24 counterclockwise.

  As shown in FIGS. 4A and 4B, in any of these cases, the absolute value of the sling load FSL increases rapidly after the winding of the sling 6 is started, and the rotating mass 24 rotates. After that, it changes in an almost constant state. When the sling 6 is wound up, the calculation device 12 is configured to rotate the rotation mass after the absolute value of the changing speed of the sling load FSL becomes smaller than a predetermined value (for example, after the time ts (ts ′) in FIG. 4). It is assumed that 24 is in a rotating state, and the sling load FSL is sampled every predetermined time (for example, 100 msec). In this case, a plurality of sling loads FSL sampled when the rotating mass 24 is rotated clockwise are stored as the sling loads FSL for calculating the compression limit load RLMP, and the rotating mass 24 is rotated counterclockwise. A plurality of sling loads FSL sampled during rotation are stored as the sling loads FSL for calculating the tension side limit load RLMS.

Next, the average value of the absolute values of the plurality of stored sling loads FSL for RLMP calculation is set as the RLMP calculation load FCRLMP, and the friction coefficient of the ball screw 23 is set using the set RLMP calculation load FCRLMP. Is so small that it can be ignored, the compression side limit load RLMP is calculated by the following equation (1).
RLMP = FCRLMP · rd · 2π / Ld (1)
Here, rd is the radius of the rotating mass 24, and Ld is the pitch of the ball screws 23. Further, as apparent from the fact that the sling load FSL is a load acting in the tangential direction of the outer periphery of the rotating mass 24, in the above equation (1), FCRLMP · rd is the torque acting on the rotating mass 24.

Similarly, the average value of the absolute values of the plurality of stored sling loads FSL for RLMS calculation is set as the RLMS calculation load FCRLMS, and the friction coefficient of the ball screw 23 is set using the set RLMS calculation load FCRLMS. If the above is so small that it can be ignored, the tension side limit load RLMS is calculated by the following equation (2).
RLMS = FCRLMS · rd · 2π / Ld (2)
In this equation (2), FCRLMS · rd is a torque acting on the rotating mass 24.

  Further, the calculation device 12 displays the compression-side limit load RLMP and the tension-side limit load RLMS calculated as described above on a display (not shown). Thereby, the operator can adjust the fastening degree of the screw 25b so that RLMP and RLMS are the same as the limit load described in the specification of the mass damper 21.

  As described above, according to the present embodiment, in the mass damper 21, as the inner cylinder 22 and the screw shaft 23a move relative to each other, the nut 23c screwed to the screw shaft 23a via the ball 23b is It rotates with respect to the screw shaft 23a and the cylindrical portion 22. Further, the rotary mass 24 covers the nut 23 c, and the axial load (the load acting on the inner cylinder 22 and the screw shaft 23 a in the axial direction) is limited by the limiting mechanism 25. In this case, until the axial load reaches a predetermined limit load, the nut 23c and the rotating mass 24 are connected to each other via the rotating sliding member 25a to rotate integrally. At that time, the rotation mass reaction force torque (torque due to the reaction force of the rotation mass 24) is transmitted to the screw shaft 23a via the nut 23c, and acts to suppress the movement of the screw shaft 23a. The degree of suppression increases as the rotational mass reaction force torque increases, and as a result, the axial load increases. In addition, when the axial load reaches the limit load, the nut 23c or the rotary mass 24 is slid with respect to the rotary sliding member 25a, thereby allowing the rotary mass 24 to rotate with respect to the nut 23c, and thereby the screw shaft 23a. By limiting the transmission of the rotational mass reaction force torque to the shaft, the axial load is limited to the limit load or less.

  Further, in the test apparatus 1, the inner cylinder 22 and the screw shaft 23 a are fixed so as not to be rotatable and immovable by the frames 2 to 5, and the rotating mass 24 is forcibly rotated using the sling 6 and the hoist 7. It is done. A sling load FSL representing torque acting on the rotating mass 24 is detected by the load cell 11. Further, based on the sling load FSL detected when the rotary mass 24 is forcibly rotated while the inner cylinder 22 and the screw shaft 23a are fixed, the calculation device 12 causes the compression-side limit load RLMP and the tension-side limit. A load RLMS is calculated.

  As described above, the axial load increases as the rotational mass reaction force torque increases. Further, in the limiting mechanism 25, the nut 23c or the rotary mass 24 is slid with respect to the rotary sliding material 25a, thereby limiting the transmission of the rotary mass reaction force torque to the screw shaft 23a. The load is limited below the limit load. As apparent from the above, the sling load FSL used for the calculation of the compression side limit load RLMP and the tension side limit load RLMS represents the torque of the rotating mass 24 when the axial load reaches the limit load. RLMP and RLMS can be calculated with high accuracy.

  Further, unlike the above-described conventional test apparatus, the rotating mass 24 is rotated while the inner cylinder 22 and the screw shaft 23a are fixed, instead of moving the screw shaft in a state where the rotating mass is held unrotatable in the outer cylinder. Therefore, the through holes, holes, and pins of the conventional test apparatus are unnecessary, and therefore the test of the limiting mechanism 25 can be easily performed. Further, since the rotary mass 24 covers the nut 23c and is provided outside, the rotary mass 24 can be easily rotated. In this case, by pulling the sling 6 wound around the rotating mass 24 with the hoist 7, the rotating mass 24 can be rotated more easily, and the test of the limiting mechanism 25 can be further facilitated.

  In addition, this invention can be implemented in various aspects, without being limited to the described embodiment. For example, in the embodiment, the hoist 7 is operated by the operator, but may be controlled by the calculation device 12. In this case, a control device for controlling the hoist 7 may be provided separately from the calculation device 12. In the embodiment, the sling load FSL is detected by the load cell 11. However, the current supplied to the hoist 7 may be detected by a sensor and may be calculated based on the detected current. Further, in the embodiment, the sling 6 and the hoist 7 are used as the rotation driving means in the present invention. However, the ring-shaped pinion gear attached to the rotating mass 24, the rack meshing with the pinion gear, and the rack reciprocatingly move. You may use the apparatus which combined the actuator to make.

  In the embodiment, the rotational mass torque parameter in the present invention is the sling load FSL, but it goes without saying that the torque acting on the rotational mass 24 itself may be used. In this case, the torque acting on the rotating mass 24 may be detected by, for example, a torque sensor. Furthermore, in the embodiment, the test apparatus 1 according to the present invention is applied to the mass damper 21 provided with the viscous body 31, but may be applied to a mass damper not provided with the viscous body. In that case, you may provide a rotation mass so that only a nut may be covered, without covering an inner cylinder. In addition, it is possible to appropriately change the detailed configuration within the scope of the gist of the present invention.

1 Test equipment 2 Front frame (fixing means)
3 Rear frame (fixing means)
4 Left frame (fixing means)
5 Right frame (fixing means)
6 Sling (Rotation drive means)
7 Hoist (Rotation drive means, tension means)
11 Load cell (Rotating mass torque parameter detection means)
12 Calculation device (calculation means)
21 Mass damper 22 Inner cylinder (cylinder part)
23a Screw shaft 23b Ball 23c Nut 24 Rotating mass 25 Limiting mechanism 25a Rotating sliding material (sliding member)
RLMP Compression side limit load (limit load)
RLMS Pull side limit load (limit load)
FSL sling load (rotational mass torque parameter)

Claims (2)

A cylindrical portion, a screw shaft partially accommodated in the cylindrical portion so as to be movable in the axial direction, and screwed to the screw shaft via a ball, and the cylindrical portion and the screw shaft move relative to each other. As a result, a nut that rotates with respect to the screw shaft and the tube portion, a rotation mass that covers the nut and that can rotate, and a load that acts on the tube portion and the screw shaft in the axial direction. In order to limit the axial load, the nut and the rotary mass are connected together via a sliding member until the axial load reaches a predetermined limit load, and the axial load is rotated. A mass damper having a limiting mechanism that allows one of the nut and the rotary mass to slide relative to the sliding member to allow the rotary mass to rotate relative to the nut. A test device mass damper testing mechanism,
Fixing means for fixing the cylindrical portion and the screw shaft so as not to rotate and move;
Rotation driving means for forcibly rotating the rotating mass;
A rotating mass torque parameter detecting means for detecting a rotating mass torque parameter representing a torque acting on the rotating mass;
Based on the rotation mass torque parameter detected when the rotation mass is rotated by the rotation drive means in a state in which the cylindrical portion and the screw shaft are fixed to be non-rotatable and non-movable by the fixing means. A calculating means for calculating a load;
A testing apparatus for mass dampers, comprising: The rotation driving means is
A sling wound around the rotating mass;
Tension means for pulling the sling wound around the rotating mass to forcibly rotate the rotating mass;
The apparatus for testing a mass damper according to claim 1, comprising:

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