JP2013167549A - Slip load test method of rotational inertia mass damer and rotational inertia mass damper - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a slip load test method of a rotational inertial mass damper capable of detecting a slip load with high accuracy in a short period time, and a rotational inertia mass damper.SOLUTION: In a method for testing a slip load between a flywheel 5 and a friction plate 6 in a rotational inertia mass damper D including a screw shaft 2, ball nuts 3, 4 screwed to the screw shaft 2, the flywheel 5, the friction plate 6 disposed between the flywheel 5 and the ball nuts 3, 4, and energization means 7 for energizing the flywheel 5 toward the friction plate 6, and for suppressing the movement of the screw shaft 2 by the inertia of the flywheel 5 rotating together with the ball nuts 3, 4 due to the movement of the screw shaft 2 in an axial direction, a load in an axial direction is made to act on the screw shaft 2 while fixing the flywheel 5.

Description

  The present invention relates to a slip load test method for a rotary inertia mass damper and a rotary inertia mass damper.

  Conventionally, as the rotary inertia mass damper, for example, an outer cylinder, a screw shaft inserted into the outer cylinder so as to be movable in the axial direction, and a circumferentially rotatable rotation within the outer cylinder and screwed into the screw shaft. A ball nut, a cylindrical flywheel that is rotatably accommodated in the outer cylinder, a friction plate interposed between the flyhole and the ball nut, and a friction plate An urging means for urging the plate toward the plate, and the movement of the screw shaft is suppressed by the inertia of the flywheel that rotates together with the ball nut by the movement of the screw shaft in the axial direction ( For example, see Patent Document 1).

  And in this rotary inertia mass damper, when excessive axial acceleration acts on the screw shaft, slip occurs between the friction plate and the flywheel, and the ball nut rotates idly. Rotational torque transmission from the flywheel to the flywheel is interrupted, and the inertial reaction force output from the rotary inertia mass damper is limited to the upper limit value. The frictional force generated between the friction plate and the flywheel can be adjusted by an urging means, and the friction plate and the urging means are so-called limiters that determine the upper limit value of the inertial reaction force of the rotary inertia mass damper. As a function.

JP 2011-144831 A

  As described above, the upper limit value of the inertial reaction force of the rotary inertia mass damper is a load acting in the axial direction on the screw shaft when the flywheel slides against the friction plate, that is, when the limiter is operated. This is a load acting on the screw shaft in the axial direction (slip load). Conventionally, to detect this slip load, the rotary inertia mass damper is actually vibrated until the flywheel slides against the friction plate, A dynamic test has been performed in which an axial load acting on the screw shaft during vibration is continuously detected and a slip load is obtained from the fluctuation of the axial load.

  In order to perform such a dynamic test, the rotary inertia mass damper must be vibrated until the flywheel slides against the friction plate. Since the flywheel slides in a very short time, it is difficult to obtain stable data with the method of detecting the slip load from the fluctuation of the axial load of the screw shaft, and it is desirable to improve the detection accuracy of the slip load. ing.

  Accordingly, the present invention has been made to solve the above-described problems, and the object of the present invention is to provide a slip load test method for a rotary inertia mass damper capable of detecting a slip load with higher accuracy in a shorter time. And providing a rotary inertia mass damper.

  In order to achieve the above-described object, the problem-solving means of the present invention includes a screw shaft, a ball nut screwed to the screw shaft, a cylindrical flywheel, the fly hole, and the ball nut. A friction plate to be interposed; and an urging means for urging the flywheel toward the friction plate, and by the inertia of the flywheel rotating together with the ball nut by the axial movement of the screw shaft In the slip load test method between the flywheel and the friction plate in a rotary inertia mass damper that suppresses movement of the screw shaft, an axial load is applied to the screw shaft while fixing the flywheel. And

  In order to achieve the above object, another problem-solving means of the present invention is accommodated in an outer cylinder, a screw shaft that is inserted into the outer cylinder so as to be movable in the axial direction, and is rotatably accommodated in the outer cylinder. A ball nut that is screwed onto the screw shaft, a cylindrical flywheel that is rotatably accommodated in the outer cylinder, and a friction plate that is interposed between the fly hole and the ball nut. And an urging means for urging the flywheel toward the friction plate, and the screw shaft is moved by inertia of the flywheel rotating together with the ball nut by the axial movement of the screw shaft. In the rotary inertia mass damper to be suppressed, a rotation blocking means for blocking the rotation of the flywheel in the circumferential direction with respect to the outer cylinder is provided.

  Therefore, the slip load can be detected by applying a load in the axial direction to the screw shaft in a state where the rotation of the flywheel is stopped and causing a slip between the flywheel and the friction plate.

  According to the present invention, it is possible to detect a slip load with higher accuracy in a shorter time.

It is a longitudinal cross-sectional view of the rotary inertia mass damper in one embodiment.

  The present invention will be described below based on the embodiments shown in the drawings. As shown in FIG. 1, the rotary inertia mass damper D according to the embodiment includes an outer cylinder 1, a screw shaft 2 inserted in the outer cylinder 1 so as to be movable in the axial direction, and a circumferential rotation in the outer cylinder 1. Ball nuts 3 and 4 that are freely accommodated and screwed onto the screw shaft 2, a cylindrical flywheel 5 that is rotatably accommodated in the outer cylinder 1 in the circumferential direction, a fly hole 5, and ball nuts 3 and 4 A friction plate 6 interposed therebetween, an urging means 7 for urging the flywheel 5 toward the friction plate 6, and rotation prevention for preventing rotation of the flywheel 5 with respect to the outer cylinder 1 in the circumferential direction. And means 8.

  When the slip load test of the rotary inertia mass damper D is performed, the rotation prevention means 8 prevents the flywheel 5 from rotating in the circumferential direction, and the rotary inertia mass damper D functions as a damper. The rotation preventing means 8 does not prevent the flywheel 5 from rotating, but allows the flywheel 5 to rotate. In a state where the rotation of the flywheel 5 is allowed, when the screw shaft 2 is moved in the left-right direction in FIG. When no slip occurs between the plate 6 and the flywheel 5, the flywheel 5 rotates with the ball nuts 3 and 4, and an inertial force is exerted to exert an inertial reaction force that suppresses the movement of the screw shaft 2. . Further, when an excessive axial load is applied to the screw shaft 2, a slip occurs between the friction plate 6 and the flywheel 5, and the inertial force of the flywheel 5 is not transmitted to the ball nuts 3, 4. The upper limit of the load acting on the shaft 2 is regulated, so that the inertial reaction force exerted by the rotary inertia mass damper D can be prevented from becoming excessive.

  Hereinafter, each part of the rotary inertia mass damper D will be described. The outer cylinder 1 is provided with two through holes 1a penetrating the meat on the side, the left end in FIG. 1 is closed by a lid 9, and an annular lid 10 is also attached to the right end in FIG. The lid 9 is provided with a bracket 9a so that the rotary inertia mass damper D can be attached to the installation location.

  A bearing 11 that prevents the screw shaft 2 from rotating is provided on the inner periphery of the lid 10. The screw shaft 2 is provided on the outer periphery of the distal end side, the shaft portion 2b provided on the right side of the screw shaft 2a in FIG. 1, and the shaft portion 2b on the right side in FIG. And a bracket 2d that is provided at the end of the base 2c and can be attached to the installation location of the rotary inertia mass damper D.

  The screw shaft 2 is inserted into the outer tube 1 with the screw portion 2a on the tip side facing inward of the outer tube 1, and the base 2c is prevented from rotating by the bearing 11, so that the outer tube 1 In contrast, movement in the axial direction is allowed. In this case, the cross-sectional shape of the base portion 2c is a shape other than a circle, the inner peripheral shape of the bearing 11 is a shape that matches the base portion 2c, and the screw shaft 2 is prevented from rotating with respect to the outer cylinder 1. Yes. The structure of the bearing 11 and the base 2c may be any structure that can prevent the screw shaft 2 from rotating. However, by providing a roller on the bearing 11 so that the roller contacts the base 2c, the outer cylinder The movement of the screw shaft 2 in the axial direction relative to 1 can be made smooth.

  The ball nuts 3 and 4 are connected together and screwed into the screw portion 2a of the screw shaft 2. The ball nuts 3 and 4 are supported by a pipe 18 mounted on the inner periphery of a ball bearing 12 fixed to the inner periphery of the outer cylinder 1, and are rotatable in the circumferential direction with respect to the outer cylinder 1. It is accommodated in the outer cylinder 1. In this embodiment, in order to withstand the load acting on the screw shaft 2, two ball nuts 3 and 4 are connected and used. However, the number of ball nuts installed is the load acting on the screw shaft 2. It is sufficient to install a number suitable for

  A flange 4a is provided at the end of the ball nut 4 on the right side in FIG. 1, and a ring 13 for holding the annular friction plate 6 on the left side in FIG. 1 is attached to the flange 4a.

  Further, a nut member 14 having a screw portion on the outer periphery is screwed to the inner periphery of the left end in FIG. 1 of the outer cylinder 1, and the nut member 14 is rotated in the circumferential direction with respect to the outer cylinder 1. Thus, it can move in the left-right direction in FIG.

  A biasing means 7 for biasing the flywheel 5 toward the friction plate 6, that is, rightward in FIG. 1 is provided on the right side of the nut member 14 in FIG. 1. The urging means 7 includes an annular pusher 15 and a plurality of coil springs 16 interposed between the pusher 15 and the nut member 14.

  More specifically, the pusher 15 has an outer periphery in sliding contact with the inner periphery of the outer cylinder 1, and a plurality of spring holes 15a opened from the left in FIG. 1 and from the inner periphery to the right in FIG. And a socket portion 15b protruding to the flywheel 5 side. One end of the coil spring 16 is inserted into each spring hole 15 a in a compressed state while being supported by the nut member 14, and urges the pusher 15 toward the friction plate 6. Therefore, the degree of compression of the coil spring 16 can be adjusted by moving the nut member 14 in the left-right direction in FIG. 1 with respect to the outer cylinder 1, and the urging force for pressing the flywheel 5 against the friction plate 6 is adjusted. Be able to.

  A ball bearing 17 is mounted on the outer periphery of the socket portion 15b of the pusher 15, and the outer periphery of the ball bearing 17 is fitted to the inner periphery on the left end of the flywheel 5 in FIG.

  The flywheel 5 has a thick cylindrical shape, and the right end in FIG. 1 is slidably fitted to the outer periphery of the socket portion 13 a protruding from the inner peripheral side of the left end in FIG. 1 of the ring 13. Furthermore, the inner diameter of the flywheel 5 is larger than the outer diameter of the ball nuts 3 and 4, and the outer diameter is smaller than the inner diameter of the outer cylinder 1. Rotation to is allowed. Thus, since the flywheel 5 is made into a cylindrical shape and the ball nuts 3 and 4 are accommodated therein, the overall length of the rotary inertia mass damper D can be shortened.

  Further, the flywheel 5 is pressed against the friction plate 6 by the urging means 7 and rotates in the circumferential direction in the outer cylinder 1 together with the ball nuts 3 and 4 in a state where no slip occurs between the flywheel 5 and the friction plate 6. Can be done.

  The urging means 7 is not limited to the above configuration, and any configuration other than the above configuration can be adopted as long as the urging unit 7 can be urged to press the flywheel 5 against the friction plate 6.

  Further, the flywheel 5 is provided with two holes 5a opened from the outer periphery at positions facing the through holes 1a provided in the outer cylinder 1, and pins P are provided in the respective holes 5a and the respective through holes 1a. It can be inserted. In addition, you may make it attach the volt | bolt which is not illustrated to the through-hole 1a and the hole 5a by making the hole 5a or the through-hole 1a into a screw hole.

  As described above, when the pin P is inserted into the hole 5a and the through hole 1a, the flywheel 5 cannot rotate in the circumferential direction with respect to the outer cylinder 1 as long as the friction plate 6 and the slip do not occur. The ball nuts 3 and 4 are also prevented from rotating with respect to the outer cylinder 1. Thus, in the rotation inertia mass damper D of this Embodiment, the rotation prevention means 8 is comprised by the pin P, the hole 5a, and the through-hole 1a.

  In order to perform a slip load test for detecting the slip load of the rotary inertia mass damper D configured as described above, the pin P is inserted into the hole 5a and the through hole 1a, and the flywheel 5 is rotated around the outer cylinder 1. In the stopped state, a load is applied to the screw shaft 2 in the axial direction. In a state where no slip occurs between the flywheel 5 and the friction plate 6, the ball nuts 3 and 4 are also prevented from rotating. Therefore, even if an axial load is applied to the screw shaft 2, the screw shaft 2 does not rotate. Does not move in the direction.

  When a load applied to the screw shaft 2 is increased and slip occurs between the flywheel 5 and the friction plate 6, the ball nuts 3 and 4 are rotatable, and the screw shaft 2 is also allowed to move in the axial direction. Thus, the load acting on the screw shaft 2 is limited to the upper limit value, and this upper limit value is the slip load. Since the slip load can be detected by detecting the axial load acting on the screw shaft 2, a load cell or strain (not shown) is applied to the screw shaft 2 or a tester (not shown) that applies a load to the screw shaft 2. A sensor capable of detecting a load, such as a gauge, is attached and can be easily detected by using the sensor.

  Accordingly, in the state where the flywheel 5 is prevented from rotating with respect to the outer cylinder 1 as described above, a load is applied to the screw shaft 2 in the axial direction, and slip occurs between the flywheel 5 and the friction plate 6. By doing so, it is possible to detect the slip load, so that it is not necessary to make a large stroke of the screw shaft 2, and if a load that causes a slip between the flywheel 5 and the friction plate 6 is applied to the screw shaft 2. Since it is good, the time taken to detect the slip load is very short.

  In addition, instead of dynamically detecting slip load as before, it is possible to detect slip load in a static environment, so stable data can be acquired, and slip load detection is possible. Accuracy can be improved.

  Further, the rotation blocking means 8 is not limited to the above-described specific configuration, but in the rotary inertia mass damper D of the present embodiment, the through hole 1a provided in the outer cylinder 1 and the flywheel 5 Since the rotation preventing means 8 is constituted by the holes 5a provided in the shaft and the pins P or bolts inserted through the through holes 1a and 5a, the structure of the rotation preventing means 8 is simple and the slip load test can be performed at low cost. Further, after the slip load test is completed, the rotary inertia mass damper D can be used as a product by removing the pin P and plugging the through hole 1a. In this case, by setting the through hole 1a as a screw hole, it is convenient that a short bolt can be easily plugged by screwing into the through hole 1a.

  The through holes 1a and the holes 5a can be installed in any number as long as they are provided in accordance with the number of pins P or bolts that can receive rotation torque acting on the flywheel 5 and prevent the flywheel 5 from rotating. Good.

  This is the end of the description of the embodiment of the present invention, but the scope of the present invention is of course not limited to the details shown or described.

DESCRIPTION OF SYMBOLS 1 Outer cylinder 1a Through-hole 2 Screw shaft 3, 4 Ball nut 5 Flywheel 5a Hole 6 Friction plate 7 Energizing means 8 Anti-rotation means D Rotation inertia mass damper P Pin

Claims (4)

A screw shaft, a ball nut screwed to the screw shaft, a flywheel, a friction plate interposed between the fly hole and the ball nut, and the flywheel attached to the friction plate The flywheel and the friction in the rotary inertia mass damper that includes the biasing means for biasing and suppresses the movement of the screw shaft by the inertia of the flywheel that rotates together with the ball nut by the axial movement of the screw shaft. In a slip load test method for detecting a slip load with a plate, an axial load is applied to the screw shaft while the flywheel is fixed to detect the axial load of the screw shaft to detect the slip load. A method for testing a slip load of a rotary inertia mass damper. An outer cylinder, a screw shaft which is inserted into the outer cylinder so as to be movable in the axial direction, a ball nut which is rotatably accommodated in the outer cylinder in the circumferential direction and is screwed to the screw shaft, and an outer cylinder A flywheel housed in a circumferentially rotatable manner, a friction plate interposed between the flyhole and the ball nut, and an urging means for urging the flywheel toward the friction plate In the rotary inertia mass damper that suppresses the movement of the screw shaft by the inertia of the flywheel that rotates together with the ball nut by the axial movement of the screw shaft, the flywheel rotates in the circumferential direction with respect to the outer cylinder. A rotation inertia mass damper, characterized in that a rotation blocking means for blocking the rotation is provided. The rotation preventing means includes a through hole provided in the outer cylinder, a hole provided in the flywheel and opposed to the through hole, and a pin or a bolt inserted into the through hole and the hole. The rotary inertia mass damper according to claim 2. The rotary inertia mass damper according to claim 3, wherein the through hole is a screw hole.

Images