JP2010107017A - Vibration control device and assembling structure thereof - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To reduce the size of a vibration control device by distributing a bearing force acting on the vibration control device having a ball screw part and by reducing the outside diameter of a screw shaft. <P>SOLUTION: The damper 1 includes: a movable base 22, into which vibration is inputted; a reaction force generation part 23, which generates a reaction force according to the vibration; and a fixed base 24, which supports the reaction force generation part 23. This reaction force generation part 23, which has the ball screw part 20 comprising two nuts 5 and a flywheel 6 provided between the two nuts, converts the vibration inputted from the movable base 22 to the two nuts 5 into rotational motion and rotates the flywheel 6 through the rotational motion. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a vibration damping device for suppressing vibrations and a structure for incorporating the vibration damping device.

  An example of the vibration damping device is a rotary inertia mass damper. The rotary inertia mass damper is a device that generates the amount of rotation of the weight member proportional to the relative displacement at both ends of the damper. From the relationship between the rotational inertia moment of the weight member and the braking force, the `` load force proportional to the relative acceleration at both ends '' is obtained. It is a device with. According to the rotary inertia mass damper, by utilizing the lever principle, there is a feature that the mass effect is 100 to 1000 times or more as compared with the actual mass of the weight.

As a specific example thereof, a vibration damping device in which a ball screw and a flywheel (rotating weight) are combined can be cited. As this type of vibration damping device, for example, the techniques described in Patent Documents 1 to 3 are available. Are known.
In the techniques described in Patent Documents 1 to 3, vibration is suppressed by rotating a flywheel using a ball screw mechanism having one nut, thereby obtaining a reaction force proportional to the relative acceleration of the input vibration. It is supposed to be. A vibration control device that combines this type of ball screw and flywheel (rotating weight) is effective because it is compact and has a large capacity (large control force) and can exhibit stable performance as an industrial product. is there.
Japanese Patent Application Laid-Open No. 07-233831 JP 2006-125110 A JP 2004-044748 A

  However, in the techniques described in Patent Documents 1 to 3, the flywheel is rotated by converting the axial force acting on the screw shaft of the ball screw mechanism into rotation by a single nut. The total acting force acting is concentrated on one nut of the ball screw mechanism. Therefore, a screw shaft having a large outer diameter is required, and there are still problems to be solved in promoting further downsizing.

  Therefore, the present invention has been made paying attention to such a problem, and it is possible to disperse the burden force acting on the vibration damping device, and to reduce the outer diameter of the screw shaft to further reduce the size. An object is to provide a vibration device and a built-in structure of the vibration control device.

  In order to solve the above-described problems, a first invention of the present invention is an input unit that receives vibration and a reaction force generation unit that generates a reaction force according to the relative acceleration of the vibration input to the input unit. And a support unit for supporting the reaction force generation unit, wherein the reaction force generation unit includes a screw shaft provided with a helical thread groove on an outer peripheral surface, and a screw shaft having the screw shaft. The screw groove has a ball screw portion having two nuts that are externally fitted through a plurality of balls and provided opposite to each other in the axial direction, and a flywheel provided between the two nuts, The vibration input from the input unit is converted into a rotational motion by the ball screw portion having the two nuts, and the flywheel is rotated by the rotational motion, whereby a reaction force according to the relative acceleration of the input vibration. Characterized by generating It is.

  According to the vibration damping device of the first invention, the ball screw portion is provided with two nuts facing each other, and the vibration input by the ball screw portion having the two nuts is converted into a rotational motion. Since the flywheel rotates by the rotational motion, a reaction force corresponding to the relative acceleration of the input vibration is generated, so the total burden force acting on the vibration damping device is distributed to the two nuts. be able to. For this reason, the outer diameter of the screw shaft can be reduced to further reduce the size.

Here, if an unexpected excessive acceleration acts on the vibration damping device, an excessive damper load force is generated. If an axial force exceeding the allowable value is generated in the screw portion that fixes the vibration damping device, the vibration damping device There is a risk of damaging not only the main body of the apparatus but also the structure or joint to which the vibration damping device is attached.
Therefore, in the vibration damping device according to the first aspect of the present invention, the flywheel is provided with a torque limiting mechanism, and the torque limiting mechanism is configured such that when the torque acting via the ball screw part exceeds a predetermined torque. In addition, it is preferable to limit the torque transmitted to the flywheel to a peak. Here, “heading” is used to mean “holding at a constant force” and “making the increment extremely small when a certain force is reached”.

  With such a configuration, even if an unexpected excessive acceleration is applied to the vibration damping device, the flywheel rotates relative to the flywheel while maintaining a predetermined torque or with an extremely small increment. It is possible to prevent or suppress the axial force exceeding the allowable value from being generated in the screw portion that fixes the vibration damping device. Therefore, damage to the vibration damping device and the structure to which the vibration damping device is attached or the joint can be prevented or suppressed.

  In the vibration damping device according to the first invention, for example, the support portion restrains and supports both rotational movement and axial movement of the screw shaft, and the input portion attaches the two nuts to the shaft of the screw shaft. If the flywheel is configured to be relatively movable in the direction and rotationally movable around the screw shaft, and the flywheel rotates with the two nuts, the reaction force of the vibration damping device according to the first invention This is suitable when the generating portion is configured as a nut rotation type.

  Further, for example, the support portion allows rotational movement of the screw shaft and restrains and supports axial movement, and the input portion allows the two nuts to move relative to each other in the axial direction of the screw shaft. If the rotational movement is constrained and connected around the shaft, and the flywheel rotates with the screw shaft, the reaction force generating portion of the vibration damping device according to the first invention is a screw shaft rotating type. It is suitable for the configuration.

Furthermore, in the vibration damping device according to the first aspect of the present invention, for example, if the position where the vibration is input to the input unit is provided in parallel with the screw shaft, the vibration damping device according to the present invention. Is suitable as a shear resistance type.
Further, for example, if the position where the vibration is input to the input unit is provided on the extension line of the screw shaft, the vibration damping device according to the first invention is configured as an axially built-in type. It is suitable for the case.

  Furthermore, the second invention of the present invention is a structure for incorporating a vibration damping device into a structure, and the input unit of the vibration damping device according to the first invention is the vibration damping device. The position where the vibration is input is used in parallel with the screw shaft, the support portion is fixed to the lower structure, and the input portion is the upper structure. And is mounted so that relative vibration is input to the support portion. The joining jig integrated with the upper structure is a jig that joins the vibration control device via a brace or a wall, and the input portion of the vibration control device has the same horizontal displacement as the upper structure. It was made to become.

  According to the built-in structure of the vibration damping device according to the second invention, for example, like a steel-based shear panel damper, it functions as a damper corresponding to shear displacement, and there is no clevis or ball joint at both ends of the vibration damping device. In addition, the overall length of the damper in the axial direction of the vibration damping device can be made compact. In addition, since the overall length of the vibration damping device according to the first invention can be configured compactly, it becomes easy to secure a space on both sides of the vibration damping device, and thus, for example, a door is provided in the space portion. An opening or an oil damper can be provided.

  In addition, another aspect of the second invention of the present invention is a structure for incorporating a vibration damping device into a structure, and as the vibration damping device, among the vibration damping devices according to the first invention, The input part uses a position where vibration is input to the input part provided on the extension line of the screw shaft, and the support part is connected to a lower structure through a mounting jig. And the input unit is attached to the end of the joining jig integrated with the upper structure, so that the vibration control device is separated above the lower structure and is one side from the center. It is located horizontally and is arranged horizontally, and is incorporated so that relative vibration is inputted from the input part to the support part.

  According to the built-in structure of another aspect of the vibration damping device according to the second invention, it functions as a damper corresponding to axial displacement, like a normal oil damper or a steel brace damper, and at both ends of the vibration damping device. If a clevis or a ball joint is used, it is possible to easily follow the deformation in the axial direction. Moreover, since the height when installed can be kept low compared to the above-described shear resistance type example, the installation height of the oil damper can be lowered even when an oil damper is additionally provided. it can. As a result, the height of the mounting jig can also be lowered, so that the bending moment acting on the lower end of the jig is reduced, and the jig can be made to have a slight configuration.

  As described above, according to the vibration damping device of the present invention, it is possible to further reduce the size of the screw shaft by reducing the outer diameter of the screw shaft by distributing the burden force acting on the vibration damping device. Moreover, according to the mounting structure of the vibration damping device according to the present invention, it becomes easy to secure a space on both sides of the vibration damping device.

  Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. 1 and 2 as appropriate. The vibration damping device of this embodiment is an example of a shear resistance type interposed between structures such as a lower beam and an upper beam (or between a floor and a wall) of a building. FIG. It is a front view which shows the outline | summary of one Embodiment of a damping device, In the same figure, one part is shown by the cross section. FIG. 2 is a ZZ cross-sectional view in FIG.

As shown in FIG. 1, the vibration damping device 1 has a fixed base 24 shown in the lower part of the figure, and the fixed base 24 supports a reaction force generator 23. The reaction force generator 23 includes a flywheel (rotating inertial body) 6 and a ball screw portion 20, and two nuts 5 of the ball screw portion 20 are connected to a movable base 22 shown in the upper part of the figure. Yes.
Specifically, the fixed base 24 includes a base plate 24b and support plates 24a and 24c provided upright at both ends of the base plate 24b, so that the front view is substantially U-shaped. The lower surface of the base plate 24b is mounted on the upper portion of the structure Sa such as a lower beam or a floor surface. The support plates 24a and 24c at both ends support the screw shaft 2 of the reaction force generating portion 23 in a both-end supported state so as to be substantially parallel to the structure Sa. The support plates 24a and 24c are supported in a state where both the rotational movement and the axial movement of the screw shaft 2 are restricted so that the screw shaft 2 is not moved when vibration is input from the movable base 22. ing.

On the other hand, the movable base 22 has a substantially flat input portion 22b provided at the upper portion, and support plates 22a and 22c attached downward to both ends of the input portion 22b. The input portion 22b is mounted on the lower surface of the structure Sb such as the upper beam or the ceiling surface in parallel with the screw shaft 2 so that relative vibration is input to the fixed base 24. It has become.
Further, the lower surfaces 22 f of the support plates 22 a and 22 c are connected to the slider 4 b of the linear guide device 4. The guide rail 4 a of the linear motion guide device 4 is fixed to the fixed base 24 side in parallel with the screw shaft 2, so that the movable base 22 is connected to the fixed base 24 via the linear motion guide device 4. Thus, smooth sliding movement in the axial direction of the screw shaft 2 is possible.

Furthermore, each support plate 22a, 22c has a through hole penetrating in the axial direction of the screw shaft 2, and the two nuts 5 of the ball screw portion 20 of the reaction force generating portion 23 are connected to the through hole in a predetermined connection. Mounted by the structure, the nut spacing is kept constant. Hereinafter, the reaction force generator 23 will be described in more detail.
The screw shaft 2 formed of a single shaft body has a spiral thread groove 3 formed on the outer peripheral surface thereof. Each nut 5 has a screw groove (not shown) corresponding to the screw groove 3 on the inner peripheral surface, and the screw shaft 2 is connected to the screw groove 3 via a plurality of balls (steel balls) (not shown). It is fitted externally so that it can rotate freely.

  The two nuts 5 facing each other have a main body portion 5A and a short cylindrical housing portion 5B. In the main body 5A, two bearing inner ring grooves 10 are formed on the cylindrical outer peripheral surface of the main body 5A in parallel with an interval in the axial direction. On the other hand, a bearing outer ring groove 12 corresponding to the bearing inner ring groove 10 of the main body part 5A of the nut 5 is formed on the inner peripheral surface of the housing part 5B, and the housing part 5B covers the outer periphery of each main body part 5A. . The housing portion 5B has an annular flange 5f, and the flange 5f is fixed to the inner end faces of the support plates 22a and 22c of the movable base 22, respectively.

  A plurality of bearing balls 14 are interposed in groove spaces formed by the bearing inner ring groove 10 and the bearing outer ring groove 12. Thus, the housing part 5B is an outer ring of the rolling bearing B, and the outer peripheral surface of the main body part 5A of each nut 5 also serves as the inner ring of the rolling bearing B. Thereby, the bearing inner ring groove 10, the bearing outer ring groove 12 and the bearing ball 14 respectively constitute a rolling bearing B, and each nut 5 is connected to the support plates 22a and 22c of the movable base 22 via the rolling bearing portion B. As a result, the distance between the nuts is kept constant, and the screw shaft 2 can move relative to the screw shaft 2 in the axial direction and can rotate around the screw shaft 2.

  Further, a cylindrical flywheel 6 having an appropriate rotational mass is fitted between the two nuts 5 so as to be rotatable around the screw shaft 2. Then, both ends of the flywheel 6 are supported so as to be sandwiched by a torque safety device 8 including a pair of bearings 9 that come into contact with both ends of the flywheel 6, and the flywheel 6 is rotated around the screw shaft 2 together with the nut 5. Rotational motion is possible, and an inertial mass effect is generated from the rotational inertia moment of the flywheel 6 and the amount of movement by the screw.

  Here, a rotary inertia mass damper using a ball screw such as the vibration damping device 1 will be briefly described. The rotary inertia mass damper has a flywheel (weight) caused by a displacement acting on the damper (vibration damping device). The inertial resistance force at that time is used to reduce the response, and the inertial resistance force (reaction force) P is obtained from the change in angular momentum generated in the weight due to the rotational moment of inertia Iθ and the rotational angular acceleration θ ”of the weight. Now, assuming that the axial displacement of the damper is x and the rotation angle of the weight is θ, the relationship is x = αθ, where α is the amount of displacement in the damper axis direction (cm / rad) with respect to the unit rotation angle of the ball screw. The load force (control force) P of the damper is expressed by the following (Expression 1), where Ld is the lead (thread pitch) of the ball screw, and α = Ld / 2π (one rotation (2π In addition to the displacement Ld).

  Here, the torque safety device 8 is attached to the flywheel 6 at a position between the nut 5 and the flywheel 6 as a torque limiting mechanism and acts on the flywheel 6 via the ball screw portion. When the torque exceeds a predetermined torque, the torque transmitted to the flywheel is limited to reach a peak. That is, when an unexpected excessive acceleration is applied from the movable base 22 which is an input unit, the flywheel 6 is slipped at a predetermined torque (relative rotation while maintaining the torque). As a result, an excessive damper load at each nut 5 portion is peaked out to prevent damage to the reaction force generating portion 23 and the like. As the torque safety device 8, for example, a so-called torque keeper (Tsubaki Emerson Corporation: TFK series or the like) can be used.

  Specifically, a rotary inertia mass damper such as the vibration damping device 1 generates a reaction force proportional to the relative acceleration at both ends of the damper. For this reason, when the relative acceleration during an earthquake becomes unexpectedly large, there is a risk of damage to the inside of the damper or the structure attached thereto due to an excessive reaction force. In view of this, the vibration damping device 1 is provided with a function of peaking the damper reaction force at a certain constant by a torque limiting mechanism (slip mechanism) built in the torque safety device 8.

That is, the force P (reaction force of the damper) acting on the ball screw is expressed by the above (Formula 1). Here, Iθθ ″ is a torque acting on the nut, which is converted into an axial force to generate a reaction force P. Since this torque T is proportional to the rotational moment of inertia, the following (formula 2), where Iθ ₀ is the rotational inertia moment of the nut and the portion fixed to the nut, and Iθ ₁ is the rotational inertia moment of the weight portion joined to the nut. It is.

If the joint between the nut and the weight is “joint that keeps the torque below T ₀ ”, T in (Expression 2) becomes (Expression 3) below.

As a result, the “torque transmitted from the weight portion” that occupies most of the rotational moment of inertia is peaked, and the reaction force P of the damper is given by (Equation 4) below. Here, T ₀ is the maximum torque transmitted from the weight to the nut.

  Therefore, by providing this torque limiting mechanism, the relationship between the relative acceleration at both ends of the damper and the reaction force becomes as shown in FIG. 3, and the reaction force reaches its peak. This can be said to be the same as the relief mechanism of the oil damper. In the oil damper, when the relative speed exceeds a certain value, the relief valve (relief valve) opens and the internal pressure of the cylinder does not become excessive, so that the reaction force of the damper reaches a peak.

Next, an example of a built-in structure of the shear resistance type vibration damping device 1 between the structures Sa and Sb such as between the lower beam and the upper beam (or between the floor and the wall) of the building will be described.
As shown in FIG. 4, in the vibration damping device 1, the lower surface of the base plate 24 b is fixed to the center of the upper surface of the lower structure Sa (the lower beam in this example). The movable base 22 at the top of the vibration damping device 1 is an upper structure of a joining jig Sb integrated with the lower ends of braces Sc provided diagonally to the left and right columns and the upper floor beam. The lower portion is mounted in parallel with the screw shaft 2 and is incorporated so that relative vibration is input to the fixed base 24.

  Here, the center position of the vibration damping device 1 (the center of the flywheel 6 and the position of the axis of the screw shaft 2) is arranged on the axis line connecting the center position and the inner end of the column beam joint. In addition, an oil damper mounting jig Dz is fixed to one end of the upper portion of the structure Sa, and the oil damper D is connected between the oil damper mounting jig Dz and the joining jig Sb. Are arranged horizontally.

  Note that a cover K having a U-shaped cross section is placed over the entire length of the vibration damping device 1 on the vibration damping device 1. The outer side surfaces of the support plates 22a and 22c of the movable base 22 serving as the outer case of the two nuts 5 are integrally coupled to the inner surface side of the U-shaped cover K. In addition, the lower end portion of the cover K is sealed.

Next, the operation | movement of this damping device 1 and its incorporation structure, an effect | action, and an effect are demonstrated.
Now, when an interlayer displacement occurs due to, for example, an earthquake or the like, the joining jig Sb (structure Sb) integrated with the brace Sc is horizontally displaced, and the movable base 22 fixed to the joining jig Sb becomes the structure Sa. It is displaced horizontally with respect to the fixed base 24 integrated with. At this time, the damping device 1 generates a shear resistance against the relative displacement between the structures Sa and Sb.

  That is, according to the vibration damping device 1, when the movable base 22, which is an input unit, vibrates relative to the fixed base 24 (vibrates left and right in FIG. 1), the movable base 22 slides along the screw shaft 2. As a result, the main body 5A of the two nuts 5 rotates. Since the flywheel 6 is attached between the two nuts 5 so as to be capable of rotating around the screw shaft 2 together with the nuts 5, the flywheel 6 rotates around the shaft together with the two nuts 5. Therefore, the linear motion of the input vibration is converted into a rotational motion by the ball screw portion 20, and by rotating the flywheel 6 by the rotational motion, a reaction force proportional to the relative acceleration of the vibration is obtained and the vibration is suppressed. Functions as a vibration damper. The relationship between the relative displacement x of the upper and lower ends of the vibration damping device 1 and the resistance force (reaction force) P is as described above.

And according to this damping device 1 and its built-in structure, it is a damper corresponding to shear displacement, for example, like a steel-based shear panel damper, and since there is no clevis or ball joint at both ends, the damper in the axial direction The overall length can be made compact.
Further, according to the vibration damping device 1 and its built-in structure, it is possible to easily secure a space on both sides of the vibration damping device 1 by making the entire length of the damper compact. It becomes possible to provide a door opening in the space portion or to dispose the oil damper D.

  Specifically, as in the built-in structure of the present embodiment, an oil damper mounting jig Dz is fixed to one end of the upper portion of the structure Sa, and between the oil damper mounting jig Dz and the joining jig Sb. In addition, if the oil damper D is disposed so as to connect each other, viscous damping can be added. In particular, if the damper (vibration control device) is a built-in type in the axial direction, only one oil damper can be provided. However, in the case of the shear resistance type as in this embodiment, a total of two on each side. This is extremely effective when it is desired to obtain viscous damping.

  Furthermore, according to this vibration damping device 1, since the input vibration is smoothly converted into a rotational motion by the ball screw portion 20, good operation is guaranteed. Moreover, the apparent mass increase effect can be enhanced by appropriately selecting the lead of the ball screw portion. In addition, according to the vibration damping device 1, the linear motion guide device 4 that connects the movable base 22 to the fixed base 24 so as to be slidable in the axial direction of the screw shaft 2 is provided. Thus, the vibration in the axial direction inputted to the two nuts 5 can be smoothly converted into the relative rotational motion with the screw shaft 2.

  Further, according to the vibration damping device 1, two nuts 5 are provided opposite to each other on the screw shaft 2, and the input vibration is converted into rotational motion by a ball screw portion having the two nuts 5. The flywheel 6 rotates by its rotational movement to obtain a reaction force corresponding to the relative acceleration of the input vibration, so that the total burden force acting on the vibration damping device 1 is applied to the two nuts 5. Dispersion (the load acting on each nut can be halved). Therefore, for example, as compared with the techniques described in Patent Documents 1 to 3 exemplified above, the outer diameter of the screw shaft 2 can be reduced to further reduce the size of the device, thereby further reducing the cost. . Moreover, since the flywheel 6 is arrange | positioned between the two nuts 5, it becomes a structure where the flywheel 6 is supported by both ends, and the support state of the flywheel 6 can be stabilized.

  Further, according to the vibration damping device 1, since the torque safety device 8 is attached to the flywheel 6, even if an unexpected excessive acceleration acts on the vibration damping device 1, the flywheel 6. Can rotate relative to each other while maintaining a predetermined torque. Therefore, it is possible to prevent or suppress the axial force exceeding the allowable value from being generated in the screw portion that fixes the vibration damping device 1. Therefore, it is possible to prevent or suppress damage to the vibration damping device 1 and the structures Sa and Sb to which the vibration damping device 1 is attached and the joint portion.

The vibration damping device and its built-in structure according to the present invention are not limited to the above-described embodiment, and various modifications can be made without departing from the spirit of the present invention.
For example, in the first embodiment described above, the housing portion 5B is an outer ring of the rolling bearing B, and the outer peripheral surface of the main body portion 5A of each nut 5 serves as the inner ring of the rolling bearing B. However, the present invention is not limited to this, and the configuration of the rolling bearing B may be separated from the nut using, for example, a commercially available bearing. However, in configuring the device more compactly, the housing portion 5B is an outer ring of the rolling bearing B as in the present embodiment, and the outer peripheral surface of the main body portion 5A of each nut 5 is the inner ring of the rolling bearing B. It is preferable to have a configuration that also serves as a combination.

  In the first embodiment, for example, the input portion 22b of the movable base 22 to which vibration is input is described as an example of a shear resistance type provided in parallel with the screw shaft 2. However, the installation posture (built-in structure) is described. Is not limited to this. Furthermore, in the above-described embodiment, the fixed base 24 that is the support portion of the reaction force generating portion 23 restrains and supports both the rotational movement and the axial movement of the screw shaft 2, and the movable base 22 that is the input portion includes two Two nuts 5 are connected so as to be relatively movable in the axial direction of the screw shaft 2 and to be rotatable around the screw shaft 2, and the flywheel 6 is rotated with the two nuts 5. Although the mold has been described as an example, the present invention is not limited to this.

  For example, you may comprise the damping device which concerns on this invention as a screw shaft rotation type like 2nd embodiment shown in FIG. That is, as shown in the figure, in the example of the second embodiment, the support plates 24a and 24c of the fixed base 24 support the screw shaft 2 via the rolling bearing 24d. Is allowed to rotate and the axial movement is restricted. The two nuts 5 do not have the housing part 5B and the rolling bearing part B, and the main body part 5A has an annular flange 5f. The flange 5f formed in the main body 5A is directly connected to the support plates 22a and 22c of the movable base 22, so that the two nuts 5 can be moved relative to each other in the axial direction of the screw shaft 2 and the screw shaft. The rotation movement is constrained around two.

  Further, the torque safety device 8 is mounted so as to rotate integrally with the screw shaft 2 via the key structure 8k, and holds the flywheel 6 so that the flywheel 6 rotates together with the screw shaft 2. This is different from the first embodiment. Thereby, in the example of this 2nd embodiment, it is a screw axis rotation type. Even in such a configuration, when the two nuts 5 are displaced in the axial direction, the screw shaft 2 rotates by reverse operation, and the flywheel 6 configured to rotate together with the screw shaft 2 rotates. The same operations and effects as the first embodiment are achieved.

  Further, for example, as in the third embodiment shown in FIG. 6, the reaction force generation unit 23 employs a nut rotation type similar to that of the first embodiment, and the input unit 22 b and the fixing unit 24 b are shown in FIG. Thus, only the position where the vibration is input is different from that of the first embodiment, and an axially built-in type provided on the extension line of the screw shaft 2 can also be used. Even with such a configuration, the same operations and effects as the first embodiment are achieved.

Here, an example of a built-in structure between the structural bodies Sa and Sb such as a space between the lower beam and the upper beam (or between the floor and the ceiling) of the axially built-in type vibration damping device 1 will be described.
As shown in FIG. 7, the axially built-in type vibration damping device 1 has a fixing portion 24 b connected to an end portion of the lower structure Sa via a mounting jig J, and the vibration damping device 1. The input portion 22b is attached to the end portion of the joining jig Sb integrated with the lower end of the brace Sc provided in a diagonal line. As a result, the vibration damping device 1 is horizontally disposed so as to be spaced apart above the lower structural body Sa and on one side of the center of the structural body Sa, and from the input portion 22b to the fixed portion 24b. It is incorporated so that relative vibrations can be input.

  Here, the height of the axis line (position of the axial center of the screw shaft 2) CL of the vibration damping device 1 is arranged on the intersection of the axial lines connecting the axial center of the joining jig Sb and the inner ends of the column beam joints. . Furthermore, an oil damper mounting jig Dz is fixed to the other side of the upper portion of the structure Sa, and the oil damper mounting jig Dz and the joining jig Sb are connected to each other. In addition, an oil damper D is horizontally disposed on the axis of the vibration damping device 1.

  As in the case of the shear resistance type, the upper part of the vibration damping device 1 is covered with a cover K having a U-shaped cross section over the entire length of the vibration damping device 1. The outer side surfaces of the support plates 22a and 22c of the movable base 22 serving as the outer case of the two nuts 5 are integrally coupled to the inner surface side of the U-shaped cover K. In addition, the lower end portion of the cover K is sealed.

  According to the built-in structure using this axially built-in type vibration damping device 1, for example, when an interlayer displacement occurs due to an earthquake or the like, the joining jig Sb (structure Sb) integrated with the brace Sc is horizontally displaced. The input portion 22b fixed to the joining jig Sb has the input portion 22b side in the axial direction (horizontal direction) with respect to the fixed portion 24b side integrated with the lower structure Sa via the mounting jig J. It is displaced to. At this time, the damping device 1 generates a shear resistance against the relative displacement between the structures Sa and Sb. As a result, as in the shear resistance type example, a reaction force proportional to the relative acceleration of vibration is obtained, and the vibration damping damper functions as a vibration damper.

  In particular, the axially built-in type vibration damping device 1 is a damper corresponding to axial displacement, such as a normal oil damper or a steel brace damper, and has clevis or the like at both ends (input portion 22b and fixed portion 24b). By using the ball joint, it is possible to easily follow the deformation in the axial direction. Moreover, since the height when installed can be kept low compared to the above-described shear resistance type, the installation height of the oil damper can be lowered even when an oil damper is provided. As a result, the height of the mounting jig can also be lowered, so that the bending moment acting on the lower end of the jig is reduced, and the jig can be made to have a slight configuration.

Further, for example, as in the fourth embodiment shown in FIG. 8, the positions of the input portion 22 b and the fixing portion 24 b are set in the axial direction built-in type provided on the extension line of the screw shaft 2 as in the third embodiment. The reaction force generator 23 may be a screw shaft rotating type as in the second embodiment. Even with such a configuration, the same operations and effects as the first embodiment are achieved.
Further, for example, as in the fifth embodiment shown in FIG. 9, in consideration of the case where an input (displacement) from a beam or the like acts from the axial direction and a direction perpendicular to the axial direction, the displacement in the perpendicular direction is canceled. A trunnion structure can be adopted.

  That is, as shown in the figure, the vibration damping device of the fifth embodiment is different from the first embodiment in that the input portion 22b of the movable base 22 has a sliding portion 22s that can slide up and down. Is different. Thereby, for example, when the structures Sa and Sb such as between the lower beam and the upper beam (or between the floor and the ceiling) of the building move relative to each other due to an earthquake or the like, the fixed base 24 moves integrally with the structure Sa such as the lower beam. On the other hand, the input portion 22b of the movable base 22 can move integrally with the structural body Sb such as the upper beam while canceling the displacement in the perpendicular direction by the sliding portion 22s that can slide up and down. Other configurations, operations and effects are the same as those in the first embodiment.

  In each of the above embodiments, the flywheel 6 is described with the example in which the torque safety device 8 is attached as the torque limiting mechanism. However, the present invention is not limited to this, and a configuration without the torque limiting mechanism may be employed. However, even if an unexpected excessive acceleration acts on the vibration damping device, the axial force exceeding the allowable value can be fixed by rotating the flywheel while maintaining the predetermined torque. In order to prevent or suppress the occurrence of the screw portion, it is preferable to attach a torque limiting mechanism to the flywheel as in the above embodiment.

  In the above description, the support portion of the vibration damping device is joined to the lower structure, and the input portion is joined to the upper structure. In the above description, the case where the ball screw portion is horizontal has been described. However, when the relative displacement other than the horizontal direction is targeted, the vibration damping device may be attached vertically or inclined.

BRIEF DESCRIPTION OF THE DRAWINGS It is a front view which shows the outline | summary of 1st embodiment (shear resistance type, nut rotation type) of the damping device which concerns on this invention, In the same figure, one part is shown by the cross section. It is ZZ sectional drawing in FIG. It is a figure which shows the relationship between the relative acceleration of the both ends of a damper by a torque limiting mechanism, and reaction force. It is a figure explaining an example of the built-in structure to the structure of the damping device of a first embodiment, The figure (a) is a front view of the principal part, The figure (b) is the figure (a). FIG. It is a figure which shows the outline | summary of 2nd embodiment (shear resistance type, screw shaft rotation type) of the damping device which concerns on this invention, The figure (a) is a front view which shows a part in a cross section, The figure (b) These are ZZ sectional drawing in the figure (a). It is a figure which shows the outline | summary of 3rd embodiment (Axial direction incorporation type, nut rotation type) of the damping device which concerns on this invention, The figure (a) is a front view which shows a part in cross section, The figure (b) These are ZZ sectional drawing in the figure (a). It is a figure explaining an example of the incorporating structure to the structure of the damping device of a third embodiment, The figure (a) is a front view of the principal part, The figure (b) is the figure (a). FIG. 3C is an enlarged view of the vibration damping device portion, and FIG. 3C is a ZZ cross-sectional view of FIG. It is a figure which shows the outline | summary of 4th embodiment (Axial direction incorporation type, screw-shaft rotation type) of the damping device which concerns on this invention, The figure (a) is a front view which shows a part in cross section, The figure (b) ) Is a ZZ cross-sectional view in FIG. It is a figure explaining 5th embodiment used as the modification of 1st embodiment, The figure (a) is a front view which shows a part in cross section, The figure (b) is Z in the figure (a). It is -Z sectional drawing.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Damping device 2 Screw shaft 3 Screw groove 4 Linear motion guide device 5 Nut 6 Flywheel 8 Torque safety device (torque limiting mechanism)
9 Rolling bearing 10 Bearing inner ring groove 12 Bearing outer ring groove 14 Bearing ball 20 Ball screw part 22 Movable base (input part)
23 Reaction force generator 24 Fixed base (support)
Sa, Sb structure Dz Oil damper mounting jig D Oil damper K Cover J Mounting jig

Claims (8)

A vibration damping device comprising: an input unit to which vibration is input; a reaction force generation unit that generates a reaction force according to the relative acceleration of vibration input to the input unit; and a support unit that supports the reaction force generation unit Because
The reaction force generating portion is provided with a screw shaft having a spiral thread groove formed on an outer peripheral surface thereof, and is externally fitted to the screw shaft through a plurality of balls and opposed to the screw shaft in the axial direction. A ball screw part having two nuts and a flywheel provided between the two nuts, and the vibration input from the input part is rotated by the ball screw part having the two nuts. The vibration damping device is characterized in that a reaction force corresponding to the relative acceleration of the input vibration is generated by turning the flywheel by the rotational motion.   The flywheel is provided with a torque limiting mechanism, and the torque limiting mechanism reaches a peak when the torque acting via the ball screw part exceeds a predetermined torque. The vibration damping device according to claim 1, wherein the vibration damping device is limited.   The support portion restrains and supports both the rotational movement and axial movement of the screw shaft, and the input portion can move the two nuts relative to each other in the axial direction of the screw shaft and can rotate around the screw shaft. The vibration damping device according to claim 1, wherein the flywheel is configured to rotate together with the two nuts.   The support portion allows rotational movement of the screw shaft and restrains and supports axial movement, and the input portion is capable of relatively moving the two nuts in the axial direction of the screw shaft and rotates around the screw shaft. 3. The vibration damping device according to claim 1, wherein the flywheel is coupled with the movement restricted, and the flywheel rotates together with the screw shaft.   5. The vibration damping device according to claim 1, wherein a position where vibration is input to the input unit is provided in parallel with the screw shaft.   5. The vibration damping device according to claim 1, wherein a position where vibration is input to the input unit is provided on an extension line of the screw shaft. A structure for incorporating a vibration damping device into a structure,
The vibration damping device according to claim 5 is used as the vibration damping device,
The support part is fixed to a lower structure, and the input part is mounted on a lower part of a joining jig integrated with the upper structure so that relative vibration is input to the support part. The built-in structure of the vibration damping device is characterized by being incorporated as described above. A structure for incorporating a vibration damping device into a structure,
The vibration damping device according to claim 6 is used as the vibration damping device,
The support portion is connected to a lower structure via a mounting jig, and the input portion is attached to an end of a joining jig integrated with the upper structure, thereby controlling the control. The vibration device is spaced horizontally above the lower structure and positioned horizontally on one side of the center so that relative vibration is input from the input unit to the support unit. Built-in structure of the vibration damping device characterized by being incorporated.

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