JP2019078320A - Inertia mass damper - Google Patents

Abstract

To provide an inertia mass damper which inhibits heat generation therein and can stabilize torque transmitted when a skid starts sliding.SOLUTION: A skid 13 of a torque limit mechanism 10 is placed in contact with a cylindrical inner surface 6a of an additional weight 6. The torque limit mechanism 10 includes a first wedge member 11, a second wedge member 12 and a spring 14. The skid 13 is pressed to the inner surface 6a of the additional weight 6 so as to transmit torque from a rotary part 24 to the additional weight 6. Further, the skid 13 is configured to slide on the inner surface 6a of the additional weight 6 when the torque transmitted from the rotary part 24 to the additional weight 6 exceeds a predetermined value.SELECTED DRAWING: Figure 2

Description

  The present invention relates to an inertial mass damper that utilizes the rotational inertia of a weight to reduce vibration between structures.

  In order to ensure the safety of building structures against earthquakes, seismic isolation or damping structures are applied to many building structures from high-rise buildings to detached houses. In recent years, an inertial mass damper that reduces the vibration between structures using the rotational inertia of a weight is being incorporated into these seismic isolation structures or damping structures (see Patent Document 1).

  The inertial mass damper includes a ball screw that converts relative vibration between structures (i.e., linear motion of a screw shaft) into rotational motion of a nut, and a cylindrical additional weight coupled to the nut. The rotational inertia force of the nut and the additional weight is amplified by the ball screw and acts between the structures as an axial inertia force (hereinafter referred to as an axial force). This axial force reduces the vibration between the structures. Depending on the shape of the ball screw lead and the additional weight, the axial inertial mass is several hundred times to several thousand times the mass of the nut and the additional weight. For this reason, the inertial mass damper is characterized in that it is possible to obtain a mass effect that is orders of magnitude greater than the mass of the nut and the additional weight.

  However, on the other hand, there is a problem in the inertial mass damper that the axial force becomes excessive when the relative acceleration between the structures is excessive, which may damage the structure or the inertial mass damper. A torque limiting mechanism is provided between the nut and the additional weight to solve this problem and limit the maximum axial force.

  The torque limiting mechanism includes a sliding member in contact with the axial end face of the cylindrical additional weight. Then, the sliding material is pressed against the additional weight by the spring so that torque can be transmitted from the nut to the additional weight, and the sliding material slides on the additional weight when the torque transmitted from the nut to the additional weight exceeds a predetermined value. Do. This limits the maximum axial force.

JP, 2011-144831, A

  However, in the conventional inertial mass damper, the sliding material contacts only the end face of the cylindrical additional weight, so the heat generated when the sliding material slides on the additional weight tends to stagnate inside the additional weight. There is. Due to heat, the dimensions of each part of the inertial mass damper change, and there is a possibility that the change in the dimensions of each part and the load generated thereby may cause the torque to vary in a predetermined value.

  Therefore, a first object of the present invention is to provide an inertial mass damper capable of suppressing heat generation inside the inertial mass damper and stabilizing torque when the sliding member starts to slide.

  Further, in the conventional inertial mass damper, in order to secure the surface pressure between the sliding member and the additional weight, it has been necessary to select a spring for pressing the sliding member with a large spring constant. There is a problem that torque management is not easy because torque management (management of torque when the sliding material starts to slide) is performed by a large load applied to the sliding material.

  Therefore, a second object of the present invention is to provide an inertial mass damper capable of facilitating torque management.

  In order to solve the first problem described above, according to a first aspect of the present invention, there is provided a motion converting mechanism for converting relative vibration between structures into rotational motion of a rotating portion, an additional weight having a cylindrical inner surface, The at least one sliding member in contact with the inner surface of the additional weight, pressing the sliding member against the inner surface of the additional weight so as to transmit torque from the rotating portion to the additional weight, and from the rotating portion And a torque limiting mechanism that causes the sliding member to slide on the inner surface of the additional weight when the torque transmitted to the additional weight exceeds a predetermined value.

  In order to solve the second problem described above, according to a second aspect of the present invention, there is provided a motion converting mechanism for converting relative vibration between structures into rotational motion of a rotating portion, an additional weight, the rotating portion, and the additional portion. The sliding member is pressed against the one side so that torque can be transmitted from the rotating part to the additional weight, and transmitted to the additional weight from the rotating part. A torque limiting mechanism for causing the sliding member to slide the one side when the torque exceeds a predetermined value, the torque limiting mechanism comprising: a first wedge-shaped member having a first inclined surface; The inertial mass damper includes a second wedge-shaped member having a second inclined surface in contact with the inclined surface and a spring for biasing the first wedge-shaped member.

  According to the first aspect of the present invention, the heat generated at the contact portion between the sliding member and the inner surface of the additional weight is dissipated to the outside through the additional weight. For this reason, the heat generation inside the inertial mass damper is suppressed, and the predetermined value of the torque (that is, the torque when the sliding member starts to slide) is stabilized. Further, since the sliding material is brought into contact with the inner surface of the additional weight, the contact area between the sliding material and the additional weight can be increased. Therefore, the predetermined value of the torque is more stable, and the durability of the sliding member is also improved.

  According to the second aspect of the present invention, the first wedge-shaped member and the second wedge-shaped member can transmit the force of the spring to the sliding member. Since a spring with a small spring constant can be selected and torque can be managed with a small load of the spring, torque management becomes easy. In addition, since a spring with a small amount of wear on the sliding member and a small spring constant can be selected, and the ratio of the load to be increased or decreased due to the change in dimensions of each part, a stable load can be transmitted to the sliding member.

It is a perspective view (a partial cross section is included) of the inertial mass damper of the 1st Embodiment of this invention. It is sectional drawing along the axis line of the inertial force generation part of the inertial mass damper of this embodiment. It is sectional drawing (a partial side view is included) along the axis line of the damping force production | generation part of the inertial mass damper of this embodiment. It is a perspective view of the 1st wedge-shaped member of the inertial mass damper of this embodiment. It is a perspective view of the 2nd wedge-shaped member of the inertial mass damper of this embodiment. It is sectional drawing in alignment with the axis line of the inertial force production | generation part of the inertial mass damper of the 2nd Embodiment of this invention. It is a perspective view of the inertial force generation part of the inertial mass damper of 2nd Embodiment.

Hereinafter, an inertial mass damper according to an embodiment of the present invention will be described based on the attached drawings. However, the inertial mass damper of the present invention can be embodied in various forms and is not limited to the embodiments described herein. This embodiment is provided with the intention to enable a person skilled in the art to fully understand the scope of the invention by making the disclosure of the specification sufficient.
First Embodiment

  FIG. 1 is a perspective view (including a partial sectional view) of an inertial mass damper according to a first embodiment of the present invention. The inertial mass damper of the present embodiment includes an inertial force generator 1 and a damping force generator 2. FIG. 2 shows a cross-sectional view of the inertial force generator 1, and FIG. 3 shows a cross-sectional view of the damping force generator 2.

  As shown in FIG. 2, the inertial force generation unit 1 includes a ball screw 3 as a motion conversion mechanism, and converts linear motion of the screw shaft 4 into rotational motion of the nut 5. An outer cylinder 6 which is an additional weight is connected to the nut 5 via a torque limiting mechanism 10. The rotational inertia force of the nut 5 and the outer cylinder 6 is amplified and converted into an inertial force in the axial direction (hereinafter referred to as an axial force) by the ball screw 3 and acts between the structures. The torque limiting mechanism 10 limits the maximum axial force in order to strike the resultant of the rotational inertia force and the viscous damping force.

  As shown in FIG. 3, the damping force generating unit 2 is one in which a viscous body 9 such as a silicone coil is filled between the fixed cylinder 7 and the damping cylinder 8. The damping cylinder 8 is connected to the outer cylinder 6. When the outer cylinder 6 rotates, the damping force generator 2 generates a viscous damping force that resists the rotation of the outer cylinder 6.

  The configuration of each part of the inertial mass damper will be described in detail below. Reference numeral 21 in FIG. 1 denotes a first connection part fixed to the first structure, and reference numeral 22 denotes a second connection part fixed to the second structure. The screw shaft 4 is non-rotatably and axially movably coupled to the first coupling portion 21 via a ball joint. The fixed barrel 7 is non-rotatably and axially non-movably coupled to the second coupling portion 22 via a ball joint. The nut 5 of the ball screw 3 is rotatably connected to the tip end portion (right end portion in FIG. 1) of the fixed barrel 7. A cylindrical housing 23 (see also FIG. 2) is rotatably connected to the tip of the fixed barrel 7 via a bearing (not shown). The nut 5 is fixed to the housing 23.

  As shown in FIG. 2, the ball screw 3 includes a large number of balls movably interposed between the screw shaft 4, the nut 5, the ball rolling groove of the screw shaft 4 and the ball rolling groove of the nut 5. And (not shown). The nut 5 is provided with a circulation part 25 such as a return pipe for circulating the ball. Since the housing 23 is fixed to the nut 5, the nut 5 and the housing 23 are the rotating portion 24. When the first connecting portion 21 and the second connecting portion 22 vibrate relative to each other, the screw shaft 4 linearly moves in the axial direction, and the rotating portion 24 rotates.

  As shown in FIG. 2, the cylindrical outer cylinder 6 surrounds the rotating portion 24. The housing is not provided on the outer side of the outer cylinder 6, and the outer cylinder 6 is in contact with the atmosphere. The outer cylinder 6 has a cylindrical inner surface 6a. A torque limiting mechanism 10 intervenes between the outer cylinder 6 and the nut 5. The torque limiting mechanism 10 includes a first wedge-shaped member 11, a second wedge-shaped member 12, a sliding member 13, a spring 14, and a lock nut 15 as a position adjusting unit.

  FIG. 4 shows the first wedge-shaped member 11. The first wedge-shaped member 11 is ring-shaped. A conical tapered surface (first inclined surface 11 a) is formed on the outer peripheral surface of the first wedge-shaped member 11. The inner circumferential surface 11c of the first wedge-shaped member 11 is cylindrical, and a first key groove 11d extending in the axial direction is formed on the inner circumferential surface 11c. On the first inclined surfaces 11 a of the first wedge-shaped member 11, a plurality of second key grooves 11 b axially formed along the first inclined surfaces 11 a are formed at equal intervals in the circumferential direction.

  As shown in FIG. 2, a first key 26 which also serves as a press of the circulating component 25 is fixed to the nut 5. The first key 26 is fitted into the first key groove 11 d of the first wedge-shaped member 11. For this reason, the first wedge-shaped member 11 is non-rotatable (that is, prevented from rotating) with respect to the nut 5 and is axially movable with respect to the nut 5.

  FIG. 5 shows the second wedge-shaped member 12. The second wedge-shaped member 12 is arc-shaped. The plurality of second wedge-shaped members 12 are arranged at equal intervals in the circumferential direction. The plurality of second wedge-shaped members 12 are arranged in a substantially ring shape, but a gap g is opened between the adjacent second wedge-shaped members 12. A conical tapered surface (second inclined surface 12 a) is formed on the inner peripheral surface of the plurality of second wedge-shaped members 12. The second inclined surface 12 a of each second wedge-shaped member 12 is formed with a recess 12 b. The second key 27 (see FIG. 2) is fitted in the recess 12b. The outer surfaces 12c of the plurality of second wedge-shaped members 12 are formed in a cylindrical shape.

  As shown in FIG. 2, the second inclined surface 12 a of the second wedge-shaped member 12 and the first inclined surface 11 a of the first wedge-shaped member 11 are in contact with each other. The second key 27 fitted in the recess 12b (see FIG. 5) of the second wedge-shaped member 12 is also fitted in the second key groove 11b (see FIG. 4) of the first wedge-shaped member 11 movably in the longitudinal direction. . For this reason, the second wedge-shaped member 12 is non-rotatable (that is, prevented from rotating) with respect to the first wedge-shaped member 11, and is movable along the first inclined surface 11a with respect to the first wedge-shaped member 11. .

  As shown in FIG. 5, a sliding member 13 is attached to the outer surface of each second wedge-shaped member 12. The sliding member 13 is formed by bending a thin plate into an arc shape. The sliding member 13 is made of resin such as PTFE (polytetrafluoroethylene), for example, and contacts the cylindrical inner surface 6 a (see FIG. 2) of the outer cylinder 6. The sliding member 13 is immovably fitted in the recess of the outer surface 12 c of the second wedge-shaped member 12. Both end portions in the circumferential direction of the sliding member 13 are fixed to the second wedge-shaped member 12 by an elongated plate-like pressing plate 13a.

  As shown in FIG. 2, the spring 14 is a large diameter disc spring, and biases the first wedge-shaped member 11 in the axial direction. In order to adjust the force of the spring 14, a lock nut 15 is provided as a position adjustment part. The lock nut 15 is screwed into the base 28 fixed to the nut 5. When the lock nut 15 is rotated, the axial position of the lock nut 15 is adjusted, and the force of the spring 14 is adjusted.

  A cylindrical spacer 29 in contact with the second wedge-shaped member 12 is fixed to the housing 23. The end face of the spacer 29 functions as a wall surface that restricts the second wedge member 12 from moving in the axial direction, and also functions as a guide surface that guides the second wedge member 12 from moving in the radial direction. In addition, although the housing 23 and the spacer 29 are separate bodies in this embodiment, the housing 23 and the spacer 29 can also be integrated.

The operation of the torque limiting mechanism 10 will be described. When the lock nut 15 is tightened and the spring 14 is compressed, the spring 14 axially biases the first wedge-shaped member 11. Axial force P ₁ of the spring 14 changes direction in the radial direction by the action of the wedge, the force P ₂ which skids 13 presses the inner surface 6a of the outer tube 6 in the radial direction. Also, the force P _{1 of the} spring 14 is increased by the action of the wedge and is transmitted to the sliding member 13. Therefore, the torque of the rotating portion 24 is transmitted to the outer cylinder 6 via the sliding member 13.

  On the other hand, when the torque transmitted from the rotating portion 24 to the outer cylinder 6 exceeds the predetermined value, the sliding member 13 starts to slide on the inner surface 6 a of the outer cylinder 6. For this reason, it is prevented that the torque more than predetermined value is transmitted to the outer cylinder 6. As shown in FIG.

In a cross section containing the center line of the screw shaft 4, the first and second inclined surfaces 11a, the angle α of the axis L ₁ of the 12a and the screw shaft 4 is set to 20 ° to 45 °. Although it depends on the coefficient of friction, the first wedge-shaped member 11 is easily locked if the angle α is less than 20 °. When the first wedge-shaped member 11 locks, the load applied to the sliding member 13 can not be adjusted. If the angle α is larger than 45 °, it is difficult to obtain the effect of boosting.

  According to the inertial mass damper of the present embodiment, the following effects can be obtained.

  Since the sliding member 13 slides on the inner surface 6 a of the outer cylinder 6, the heat generated at the contact portion between the sliding member 13 and the inner surface 6 a of the outer cylinder 6 is transmitted to the outer cylinder 6 and dissipated to the outside. For this reason, heat generation inside the inertial mass damper is suppressed, and a predetermined value of torque (torque when the sliding member starts to slide) is stabilized. Further, since the sliding member 13 is in contact with the inner surface 6 a of the outer cylinder 6, the contact area between the sliding member 13 and the outer cylinder 6 can be increased. Therefore, the predetermined value of the torque is more stable, and the durability of the sliding member 13 is also improved.

  Since the torque limiting mechanism 10 includes the first wedge-shaped member 11, the second wedge-shaped member 12, and the spring 14, the force of the spring 14 can be increased and transmitted to the sliding member 13 by the action of the wedge. Therefore, the spring 14 having a small spring constant can be selected, and torque can be managed with a small load of the spring 14. Further, even if the sliding member 13 wears, the reduction in load is small because the first wedge-shaped member 11 and the second wedge-shaped member 12 follow. Conversely, even if the load on the sliding member 13 is increased due to expansion such as heat generation, the first wedge-shaped member 11 and the second wedge-shaped member 12 escape, so that the appropriate load can be maintained. Furthermore, since the direction of the axial force of the spring 14 can be changed in the radial direction by the action of the wedge, disposing the torque limiting mechanism 10 in a narrow space between the outer surface of the rotating portion 24 and the inner surface 6a of the outer cylinder 6 Can.

  Since the first wedge-shaped member 11 is ring-shaped and the plurality of second wedge-shaped members 12 are arranged in the circumferential direction of the first wedge-shaped member 11, the plurality of sliding members 13 are all around the inner surface 6 a of the outer cylinder 6 It is possible to push evenly, and the predetermined value of torque becomes more stable. Since the gap g is formed between the adjacent second wedge-shaped members 12, the second wedge-shaped member 12 also easily dissipates heat.

The first wedge-shaped member 11 and the second wedge-shaped member 12 are prevented from rotating around the rotating portion 24 because the first wedge-shaped member 11 is locked to the rotating portion 24 and the second wedge-shaped member 12 is locked to the first wedge-shaped member 11. To rotate.
Second Embodiment

  6 and 7 show an inertial mass damper according to a second embodiment of the present invention. As shown in FIG. 6, in the second embodiment, the configuration of the spring 31 of the torque limiting mechanism 10 and the set screw 32 as a position adjustment unit is different from that of the first embodiment. The configurations of the first wedge-shaped member 11, the second wedge-shaped member 12, the sliding member 13, the outer cylinder 6, the screw shaft 4, the nut 5, the housing 23 and the spacer 29 of the torque limiting mechanism 10 are the same as in the first embodiment. The same reference numerals are given and the description thereof is omitted.

  In the second embodiment, a plurality of small diameter laminated disc springs are used as the spring 31 of the torque limiting mechanism 10. A plurality of springs 31 are arranged at equal intervals in the circumferential direction. A ring-shaped spring base 33 (see also FIG. 7) is fixed to the nut 5. In the spring base 33, a plurality of spring receiving holes 33a are opened at equal intervals in the circumferential direction. The spring 31 is accommodated in the spring accommodation hole 33a. The set screw 32 is screwed into the female screw of the spring receiving hole 33a. By adjusting the tightening amount of the set screw 32, the force of the spring 31 can be adjusted.

  The present invention is not limited to being embodied in the above-described embodiment, and can be embodied in various embodiments without departing from the scope of the present invention.

  In the above embodiment, the nut of the ball screw is rotated and the nut is used as the rotating portion. However, the screw shaft may be rotated and the screw shaft may be used as the rotating portion.

  In the above embodiment, although the inertial force damper is provided with the inertial force generator and the damping force generator, the damping force generator can be omitted and only the inertial force generator can be used.

  Although the additional weight is cylindrical in the above embodiment, the additional weight may be disk-like.

  In the above embodiment, the sliding member and the second wedge-shaped member are separated, and the sliding member is provided on the second wedge-shaped member. However, the sliding member and the second wedge-shaped member can be integrated.

  In the above embodiment, the second wedge-shaped member is divided into a plurality of pieces, but the second wedge-shaped member may be ring-shaped and a slit may be provided so as to extend outward.

DESCRIPTION OF SYMBOLS 1 ... inertia force generation part, 2 ... damping force generation part, 3 ... ball screw (motion conversion mechanism), 4 ... screw axis, 5 ... nut, 6 ... outer cylinder (additional weight), 6a ... inner surface, 10 ... torque limitation Mechanism 11 11 first wedge-shaped member 11a 1st inclined surface 12 12 second wedge-shaped member 12a 2nd inclined surface 13 slipper 24 rotation part 26 1st key 27 27 second Key

Claims (6)

A motion conversion mechanism that converts relative vibration between structures into rotational motion of the rotating part;
An additional weight having a cylindrical inner surface,
The at least one sliding member in contact with the inner surface of the additional weight, pressing the sliding member against the inner surface of the additional weight so as to transmit torque from the rotating portion to the additional weight, and from the rotating portion And a torque limiting mechanism for causing the sliding member to slide on the inner surface of the additional weight when the torque transmitted to the additional weight exceeds a predetermined value. The torque limiting mechanism
A first wedge-shaped member having a first inclined surface;
A second wedge-shaped member having a second inclined surface in contact with the first inclined surface;
The inertia mass damper according to claim 1, further comprising: a spring biasing the first wedge-shaped member in the axial direction of the rotating portion. The first wedge-shaped member is ring-shaped,
The inertial mass damper according to claim 2, wherein the plurality of second wedge-shaped members are arranged in the circumferential direction of the first wedge-shaped member. The first wedge-shaped member is locked to the rotating portion;
The inertial mass damper according to claim 2 or 3, wherein the second wedge-shaped member is fixed to the first wedge-shaped member. A motion conversion mechanism that converts relative vibration between structures into rotational motion of the rotating part;
An additional weight,
It has at least one sliding member in contact with any one of the rotating portion and the additional weight, presses the sliding member against the one side so that torque can be transmitted from the rotating portion to the additional weight, and from the rotating portion And a torque limiting mechanism that causes the sliding member to slide the one side when the torque transmitted to the additional weight exceeds a predetermined value.
The torque limiting mechanism
A first wedge-shaped member having a first inclined surface;
A second wedge-shaped member having a second inclined surface in contact with the first inclined surface;
And a spring for biasing the first wedge-shaped member. The sliding member is in contact with any one of the cylindrical outer surface of the rotating portion and the cylindrical inner surface of the additional weight,
The inertial mass damper according to claim 5, wherein the first wedge-shaped member and the second wedge-shaped member change the direction of the force of the spring from an axial direction of the rotating portion to a radial direction of the rotating portion.

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