JP5696881B2 - Vibration control device using inertial mass damper - Google Patents

Description

  The present invention relates to a vibration damping device using an inertial mass damper.

  2. Description of the Related Art Conventionally, a mechanism (hereinafter referred to as an inertia mass damper) that exhibits an inertia mass effect that is orders of magnitude greater than the actual mass by rotating the weight using the inertia moment of the weight is known. In such an inertial mass damper, a reaction force proportional to the relative acceleration at both ends of the damper is generated.Therefore, an excessive reaction force may act upon unexpected input, which may damage the damper body or the body structure attached to the damper body. there were. Therefore, for example, Patent Document 1 discloses a method of providing an overload prevention function by joining a rotary weight and a ball screw mechanism via a friction material.

  In Patent Document 1, a rotary weight is connected to a vibration transmission mechanism so that torque can be transmitted between the ball screw mechanism and the rotary weight as a vibration transmission mechanism that converts relative vibrations into rotational motion and transmits the rotation to the rotary weight. And a torque limiting mechanism that limits the torque transmission by rotating the rotary weight relative to the vibration transmitting mechanism when the torque transmitted between them exceeds a predetermined limit value. Inertia mass dampers using the frictional force of the sliding material or using a general-purpose torque holding device are described.

  By the way, as a vibration reduction mechanism, an additional spring that elastically supports the structure with respect to the support, and a rotary inertia mass damper that generates a rotation inertia mass by the rotation of the rotating body, the structure and the support that supports the structure. One having an additional vibration suppression mechanism interposed in series between them is widely known (see, for example, Patent Document 2).

JP 2010-19347 A JP 2008-101769 A

However, the conventional vibration control device has the following problems.
That is, in the inertial mass damper of Patent Document 1, the overload prevention mechanism using the friction material of the prior art can provide a high performance characteristic that the reaction force can be peaked out without causing residual deformation. Since it incorporates a rotating friction mechanism, there is a problem that such an overload prevention function becomes expensive, and there is a demand for one that exhibits the same effect while using an inexpensive inertial mass damper. There was room for improvement.
Moreover, in the vibration reduction mechanism shown in Patent Document 2, a large response reduction effect can be obtained by synchronizing with the natural frequency of the structure. For this reason, considering the non-linearity of the additional spring, the damper load force can be significantly reduced without changing the maximum response value of the structure so much, so a specific structural frame configuration is required to realize this. It was.

  The present invention has been made in view of the above-described problems, and an object thereof is to provide a vibration damping device using an inertial mass damper that can reduce the burden of the inertial mass damper with an inexpensive structure.

In order to achieve the above object, a vibration damping device using an inertial mass damper according to the present invention uses an inertial mass damper interposed in a frame surrounded by adjacent columns of a building and vertically adjacent beams. A vibration damping device having one end fixed to the first beam of the upper floor beam and the lower floor beam and the other end slidably provided to the other second beam. a brace having one end fixed to the second beam and the other end provided with an inertial mass damper is fixed to the other end of the brace, the brace and the inertial mass damper is joined in series, brace axially yielding It is characterized by comprising a brace damper or a friction damper .

  In the present invention, when the first beam and the second beam are relatively displaced due to earthquake vibration or the like, the brace and the second beam are relatively displaced via the inertia mass damper. For example, a brace having a damping damper function such as a shaft yielding brace damper or a friction damper is used. Generation of a reaction force is prevented. Therefore, the load of inertia of the inertia mass damper can be stopped, and a fail-safe mechanism similar to the overload prevention mechanism can be realized.

In the vibration damping device using the inertial mass damper according to the present invention, it is preferable that an additional damping mechanism supported to the second beam is joined in parallel to the inertial mass damper.
In this case, since the vibration can be attenuated by an additional damping mechanism such as an oil damper with respect to the inertia mass damper having no static rigidity, residual deformation can also be suppressed.

In the vibration damping device using the inertial mass damper according to the present invention, it is preferable that an additional spring elastically supported with respect to the second beam is joined in parallel to the inertial mass damper.
In this case, since the resilience is imparted to the inertial mass damper having no static rigidity by the elasticity of the additional spring, residual deformation can be suppressed.

  According to the vibration damping device using the inertial mass damper of the present invention, the load of the inertial mass damper is suppressed by the braces arranged in series and the reaction force is excessively generated, and the load of the inertial mass damper is reduced. Therefore, it is not necessary to provide an overload prevention mechanism for the inertial mass damper. Therefore, since it becomes possible to incorporate a vibration control device in a building by a simple mechanism using members that are generally used, it is possible to reduce costs.

It is an elevation sectional view showing the composition of the vibration damping device by a 1st embodiment of the present invention. It is an elevation sectional view showing the composition of the vibration damping device by a 2nd embodiment of the present invention. It is an elevation sectional view showing the composition of the vibration damping device by a 3rd embodiment of the present invention. It is an elevation sectional view showing the composition of the vibration damping device by a 4th embodiment of the present invention. It is the sectional view on the AA line shown in FIG. It is an elevation sectional view showing the composition of the damping device by the modification of a 1st embodiment.

  Hereinafter, a vibration damping device using an inertial mass damper according to an embodiment of the present invention will be described with reference to the drawings.

(First embodiment)
As shown in FIG. 1, the vibration damping device 1A according to the first embodiment includes a column 2 (2A, 2B) adjacent to a building and a beam 3 (upper beam 3A, lower beam 3B) adjacent in the vertical direction. It is installed in the frame R that is surrounded. That is, the damping damper device 1A is fixed to the upper beam 3A (first beam) and slidable in the horizontal direction with respect to the lower beam 3B (second beam) within the frame R. A V-shaped brace 4 is provided, the V-shaped apex 4a of the brace 4 and the lower beam 3B are connected via an inertia mass damper 5, and the V-shaped apex 4a and the other column 2 (second column) 2B) is connected via an oil damper 6 (additional damping mechanism).

The brace 4 has a pair of V-shaped upper ends 4b, 4b (fixed ends) fixed integrally to the corners of the frame R (joint portion between the column 2 and the upper beam 3A), and a V-shaped apex 4a. (Sliding end) is connected to a slidable joining jig 10 by a linear guide 7 provided on the upper surface 3a of the lower beam 3B. Further, as the brace 4, an axial yield type brace damper (for example, “CS damper” of Shimizu Corporation) or a friction damper is employed.

  The V-shaped apex 4a of the brace 4 is fixed to the joining jig 10, and one end 5a in the axial direction (stroke direction) of the inertial mass damper 5 is connected to one end 10a in the sliding direction X, and further sliding. One end 6a in the axial direction of the oil damper 6 is connected to the other end 10b in the direction X. The joining jig 10 is configured to be displaced along the linear guide 7 provided on the lower beam 3B.

  The linear guide 7 is a guide rail that is fixed to the upper surface 3a of the lower beam 3B so that its longitudinal direction is parallel to the material axis direction of the lower beam 3B, and the joining jig 10 slides along this rail. Supported as possible.

  The inertia mass damper 5 has one end 5a in the axial direction (right side in FIG. 1) fixed to the brace 4 via the joining jig 10, and the other end 5b on the other side (left side in FIG. 1) is fixed to the first damper. It is connected to the lower beam 3B through the tool 8. At this time, the first damper mounting jig 8 is fixed to the upper surface 3a of the lower beam 3B, and restrains the displacement of the inertial mass damper 5 in the axial direction.

  The oil damper 6 is interposed between members that are displaced relative to each other (between the upper beam 3A and the lower beam 3B), has a load force proportional to the relative speed at both ends, and has an axial direction relative to the inertial mass damper 5. It is on the coaxial line. In other words, the oil damper 6 has a function of transmitting the amplified displacement generated in the inertial mass damper 5 at the time of tuning and absorbing the energy of the amplified displacement, and one end of the axial direction (left side in FIG. 1). 6 a is fixed to the brace 4 via the joining jig 10, and the other (right side in FIG. 1) other end 6 b is connected to the lower beam 3 B via the second damper attaching jig 9. At this time, the second damper mounting jig 9 is fixed to the upper surface 3a of the lower beam 3B, and restrains the displacement of the oil damper 6 in the axial direction.

Next, the operation of the above-described vibration damping device 1A will be described based on the drawings.
As shown in FIG. 1, in the vibration damping device 1 </ b> A, when the upper beam 3 </ b> A and the lower beam 3 </ b> B are relatively displaced due to earthquake vibration or the like, the brace 4 and the lower beam 3 </ b> B are relatively displaced via the inertia mass damper 5. It will be. And, by using the brace 4 having the function of a damping damper, even if the load of the inertial mass damper 5 is increased, it is prevented that the load is capped by the braces 4 arranged in series and an excessive reaction force is generated. Is done. Therefore, the load of inertial mass damper 5 can be peaked, and a fail-safe mechanism similar to the overload prevention mechanism can be realized.

  Further, in the vibration damping device 1A, since the oil damper 6 supported by the lower beam 3B is joined in parallel to the inertia mass damper 5, the inertia mass damper 5 having no static rigidity is connected to the inertia mass damper 5. Thus, the vibration can be damped by the oil damper 6 forming the additional damping mechanism, and the residual deformation can be suppressed.

  As described above, in the vibration damping device using the inertial mass damper according to the first embodiment, it is possible to suppress the occurrence of an excessive reaction force due to the load of the inertial mass damper 5 being capped by the braces 4 arranged in series. Therefore, it is not necessary to provide an overload prevention mechanism in the inertial mass damper 5. Therefore, the vibration damping device 1 can be incorporated into the building by a simple mechanism using a member that is generally used, and thus the cost can be reduced.

  Next, other embodiments will be described with reference to the accompanying drawings. However, the same or similar members and parts as those of the above-described first embodiment are denoted by the same reference numerals and description thereof is omitted. A configuration different from the embodiment will be described.

(Second Embodiment)
As shown in FIG. 2, the vibration damping device 1 </ b> B according to the second embodiment has an inverted V-type brace 4 in which the brace 4 is inverted in the vertical direction arranged in the plane of the frame R.
That is, the brace 4 has a pair of lower end portions 4c, 4c (fixed ends) fixed integrally to corner portions of the frame R (joint portion between the column 2 and the lower beam 3B), and a V-shaped apex portion 4d (slider). (Moving end) is connected to the joining jig 10. Here, the joining jig 10 is in a state where it is not joined to the lower surface 3b of the upper beam 3A, the V-shaped apex 4d of the brace 4 is fixed, and an inertial mass is attached to one end 10a in the sliding direction X. One end 5a in the axial direction (stroke direction) of the damper 5 is connected, and one end 6a in the axial direction of the oil damper 6 is connected to the other end 10b in the sliding direction X.

The inertia mass damper 5 has one end 5a (right side in FIG. 1) in the axial direction fixed to the brace 4 via the joining jig 10, and the other end 5b on the other side (left side in FIG. 1) is the first damper. It is connected to the upper beam 3 </ b> A via the mounting jig 8.
On the other hand, one end 6a in the axial direction (left side in FIG. 1) of the oil damper 6 is fixed to the brace 4 via the joining jig 10, and the other end 6b on the other side (right side in FIG. 1) is attached to the second damper. It is connected to the upper beam 3A via a jig 9.

  In the vibration damping device 1B according to the second embodiment, as in the first embodiment described above, when the upper beam 3A and the lower beam 3B are relatively displaced due to earthquake vibration or the like, the brace 4 and the upper beam 3A. Are relatively displaced via the inertial mass damper 5. And since the brace 4 having the function of a vibration damper is used, even if the load of the inertial mass damper 5 is increased, it is prevented that the load is capped by the braces 4 arranged in series and an excessive reaction force is generated. There is an effect and effect.

(Third embodiment)
As shown in FIG. 3, the vibration damping device 1 </ b> C according to the third embodiment is a configuration obtained by partially changing the configuration of the vibration damping device 1 </ b> A (FIG. 1) according to the first embodiment described above. 4 is provided with an oil damper with a relief mechanism (hereinafter referred to as “brace oil damper 11”), and in addition to the oil damper 6 provided between the joining jig 10 and the lower beam 3B in the first embodiment described above. Instead, a restoring spring 12 (additional spring) is provided. The inertial mass damper 5 has the same configuration as that of the first embodiment, and a detailed description thereof is omitted here.

The brace oil damper 11 is incorporated in the straight portions 41 and 42 in a state in which the axial direction thereof is directed to the respective material axial directions J of the pair of straight portions 41 and 42 constituting the brace 4. By providing a relief mechanism such as a valve, it has the characteristic of preventing overload.
Here, when the length dimension of the brace 4 is large, a steel material (steel pipe or the like) is integrated and extended in the axial direction of the brace oil damper 11, and a clevis or a ball joint is provided at both ends thereof. good.

  The restoring spring 12 has one end 12a (left side in FIG. 1) in the expansion / contraction direction (biasing direction) of the spring fixed to the brace 4 via the joining jig 10, and the other end (right side in FIG. 1). 12b is connected to the lower beam 3B via the second damper mounting jig 9.

In the vibration damping device 1 </ b> C according to the third embodiment, even if a relative displacement occurs and the load on the inertial mass damper 5 increases, the damping device 1 </ b> C is arranged in series with respect to the inertial mass damper 5 via the joining jig 10. Since it reaches a peak due to the relief load of the brace 4, the reaction force can be suppressed, and there is an effect that an excessive reaction force is not generated.
Further, since a restoring spring 12 elastically supported with respect to the upper beam 3A is joined in parallel to the inertia mass damper 5, the inertia mass damper 5 and the brace oil damper 11 having no static rigidity are joined. Since resilience can be imparted by the elasticity of the restoring spring 12, residual deformation can be suppressed.

(Fourth embodiment)
Next, as shown in FIGS. 4 and 5, the vibration damping device 1D according to the fourth embodiment is the same as that between the upper beam 3A and the lower beam 3B in the first to third embodiments described above. However, instead of this, it is configured to be arranged over a plurality of layers (two layers in the fourth embodiment) such as two or three layers of the building.
In this case, an intermediate beam 3C on the intermediate floor is provided between the upper beam 3A and the lower beam 3B, and the position of the intermediate beam 3C is perpendicular to the frame so as not to interfere with the vibration control device 1D. It is arranged at a position shifted to.

The brace 4 includes an upper brace 4A provided on the upper frame Ra between the upper beam 3A and the intermediate beam 3C, and a lower brace 4B provided on the lower frame Rb between the intermediate beam 3C and the lower beam 3B.
The upper brace 4A has a V shape, a pair of upper end portions 4b and 4b are fixed to the upper beam 3A, and the V-shaped apex portion 4a slides on the intermediate beam 3C via the first joining jig 10A. It is supported movably. The upper brace 4A employs a brace damper such as a steel damper or a friction damper.
The lower brace 4B has a substantially inverted V shape, a pair of lower end portions 4c and 4c are fixed to the lower beam 3B, and a V-shaped apex portion 4d is connected to the intermediate beam 3C via the second joining jig 10B. And is slidably supported. The lower brace 4B employs an earthquake-resistant brace made of a member that does not yield.

The first joining jig 10A connected to the upper brace 4A is disposed at the center of the intermediate beam 3C in the material axis direction, and a linear guide 7 that is slidably supported is provided on the side of the intermediate beam 3C.
The second joining jig 10B connected to the lower brace 4B is an inertial mass damper with respect to the first joining jig 10A, ie, a position closer to the column 2A than the first joining jig 10A in the material axis direction of the intermediate beam 3C. 5 and the linear guide 7 is provided on the side of the intermediate beam 3C.
Therefore, the first joining jig 10A and the second joining jig 10B are configured to be slidably engaged with the respective linear guides 7 in a lateral state.

  The inertial mass damper 5 has a function of amplifying the relative displacement between the lower beam 3B and the upper beam 3A at the time of tuning, and has a damping mechanism, and one end 5a in the axial direction (right side in FIG. 4) has a first joint. It is fixed to the upper brace 4A via the jig 10A, and the other end 5b (left side in FIG. 4) is fixed to the lower brace 4B via the second bonding jig 10B.

Further, the end (the other end 10 b) opposite to the inertial mass damper 5 in the sliding direction X in the first joining jig 10 </ b> A is connected to the column 2 (second column 2 </ b> B) via the restoring spring 12. .
The restoring spring 12 has one end 12a (left side in FIG. 1) of the spring expansion / contraction direction P (biasing direction) fixed to the upper brace 4 via the first joining jig 10A, and the other (right side in FIG. 1). ) End 12b is connected to the second pillar 2B via the connecting member 13.

  In the vibration damping device 1D according to the fourth embodiment configured as described above, the displacement acting on the inertial mass damper 5 can be earned by being installed across two layers, that is, the brace 4 and the inertial mass damper. Since the relative displacement generated in the present vibration damping device in which 5 and 5 are arranged in series is increased, the damping effect can be increased. This is the same effect as when the equivalent damping coefficient and inertial mass increase when the displacement magnifying mechanism is provided in the vibration damping device.

As mentioned above, although the embodiment of the vibration damping device using the inertial mass damper according to the present invention has been described, the present invention is not limited to the above embodiment, and can be appropriately changed without departing from the gist thereof. is there.
For example, in the first embodiment and the second embodiment, the oil damper 6 is provided in parallel with the inertia mass damper 5, but not limited thereto, for example, an inertia mass damper having a damping function is adopted. In this case, an oil damper is not necessary. Further, the inertia mass dampers 5 may be arranged on both sides of the joining jig 10.

  Further, in the case where the vibration damping device is installed across a plurality of layers (two layers), the brace 4 made of a steel damper or an oil damper is arranged on the upper frame Ra on the upper layer side in the fourth embodiment. What is necessary is just to arrange | position to either one of upper frame Ra or lower frame Rb.

Furthermore, the vibration damping device according to the present embodiment is not limited to the application of the new structure, and the braces 4 and the like may be joined to the column beams 2 and 3 of the existing structure. .
Further, as shown in FIG. 6, a steel frame 14 is provided in the plane of the frame R of the existing column beam, and the vibration damping device according to the above-described embodiment (in FIG. 6, the vibration damping device according to the first embodiment is provided). By arranging 1A), the same effect can be obtained for both RC structures and steel structures. Note that the gap between the steel frame 14 and the frame (column beam) is filled with mortar or the like.

  In addition, it is possible to appropriately replace the constituent elements in the above-described embodiments with well-known constituent elements without departing from the spirit of the present invention, and the above-described embodiments may be appropriately combined.

1A-1D Vibration control device 2, 2A, 2B Column 3A Upper beam (first beam)
3B Lower beam (second beam)
3C Intermediate beam 4 Brace 5 Inertial mass damper 6 Oil damper (additional damping mechanism)
7 Linear guide 8 First damper mounting jig 9 Second damper mounting jig 10, 10A, 10B Joining jig 11 Oil damper for braces 12 Restoration spring (addition spring)
R frame

Claims (3)

A vibration damping device using an inertial mass damper interposed in a frame surrounded by adjacent pillars of a building and beams adjacent in the vertical direction,
A brace having a function of a damping damper having a fixed end fixed to the first beam of either the upper beam or the lower beam and a sliding end slidably provided to the other second beam; ,
An inertia mass damper having one end fixed to the second beam and the other end fixed to the sliding end of the brace;
With
The brace and the inertia mass damper are joined in series ,
The said brace is comprised by the axial yield type brace damper or the friction damper , The damping device using an inertial mass damper characterized by the above-mentioned.   2. The vibration damping device using the inertial mass damper according to claim 1, wherein an additional damping mechanism supported to the second beam is joined in parallel to the inertial mass damper. 3.   2. The vibration damping device using the inertial mass damper according to claim 1, wherein an additional spring that is elastically supported with respect to the second beam is joined to the inertial mass damper in parallel.

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