JP2017020531A - Vibration control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vibration control device capable of effectively suppressing floating of a weight in a tuned mass damper (TMD).SOLUTION: To a weight 1 of a TMD, provided is a damper 3 of which one end part is fixed to a weight 1 of a TMD, and the other end part is fixed to a structure and deforms in a vertical direction, and in which an attenuation coefficient is made larger as the deformation is made larger.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a vibration damping device using a pendulum type tuned mass damper (TMD).

  In recent years, as a vibration control technology for high-rise buildings against long-period and long-term ground motions, TMD (tuned mass damper) for wind motion, which has been used as a vibration control technology for minute vibrations of buildings caused by strong winds, etc. Various types of earthquake TMDs have been developed that have been expanded in size and increased in stroke to extend the scope of application to control of large amplitude vibrations of earthquakes (for example, Patent Document 1).

  According to the TMD for earthquakes, since the installation location is on the roof or the top floor of the building, it is possible to increase the degree of freedom in planning the building, and also when damping and reinforcing existing high-rise buildings. There is an advantage that the construction can be performed while using the building.

JP 2011-27136 A

By the way, the conventional earthquake TMD is generally a pendulum type device in which a large weight 50 is suspended by a wire or a steel rod 51 as shown in FIG.
According to the pendulum type earthquake TMD having the above-described configuration, the suspension of the weight 50 is adjusted to synchronize the TMD period with the natural period in the horizontal direction of the building 52, thereby resonating the TMD and vibrating the building. Energy can be efficiently collected in the TMD and absorbed by the energy absorbing device 53 such as an oil damper installed in the TMD to suppress the shaking of the building 52.

At this time, in the above-described earthquake TMD, the weight 50 vibrates in the vertical direction due to the vertical earthquake motion, and the TMD may be lifted, which may cause the performance degradation or breakage of the TMD.
Therefore, in order to suppress the vertical vibration of the weight 50, the vertical vibration of the weight 50 is reduced by connecting the building 52 and the TMD weight 50 with the oil damper 54 in the vertical direction. .

However, in the earthquake TMD, when the weight 50 swings, as shown in FIG. 8, the vertical oil damper 54 is angled with respect to the vertical direction as the weight 50 moves away from the origin. and theta inclined, this result vertical component F _v of the damping force F of the oil damper 54, was also F _v = F cos ² disadvantageously reduced to theta.

  This invention is made | formed in view of the said situation, and makes it a subject to provide the damping device which can suppress effectively the lifting of the weight in pendulum type TMD.

  In order to solve the above-described problem, a vibration damping device according to the present invention described in claim 1 includes a TMD weight having one end connected to the weight and the other end connected to a structure. A damper is provided which is deformed in the vertical direction by movement and whose damping coefficient increases as the deformation increases.

  According to a second aspect of the present invention, there is provided the bypass pipe according to the first aspect, wherein the damper is an oil damper, and the bypass pipe communicates the front and rear of the piston in the cylinder filled with the working fluid. A shut-off valve is provided for narrowing the flow path of the bypass pipe as the deformation between and increases.

  Furthermore, the invention described in claim 3 is the invention described in claim 1 or 2, wherein the TMD is a pendulum type, and a concave portion having an inner wall formed in a conical surface is formed at the bottom of the weight. The end of the damper is connected to the top of the recess.

  In the vibration damping device according to any one of claims 1 to 3, the damper gradually inclines in the horizontal direction as the TMD weight moves in the horizontal direction and moves away from the origin position (vertical position) during an earthquake. As a result, the vertical component of the damping force is reduced, but the deformation of the damper is also increased and the damping coefficient is gradually increased, so that the vertical component of the damping force can be increased and canceled out. .

  As a result, according to the vibration damping device, even if the horizontal displacement of the weight of the TMD increases during a large earthquake, the lifting of the weight can be effectively suppressed.

  In the invention according to claim 3, when the weight swings in the horizontal direction during an earthquake, the inclination angle of the damper is smaller than that when the pin is coupled to the bottom of the weight. The vertical component of the damping force can be increased. Therefore, coupled with the fact that the damping coefficient increases as the deformation increases, the lifting of the weight can be more effectively suppressed.

It is the schematic for demonstrating one Embodiment of this invention. (A) is a graph showing the relationship between the deformation of the weight of the oil damper and the damping coefficient ratio α in the embodiment, and (b) is the horizontal deformation of the weight and the damping coefficient ratios α _v and α _{h in} the embodiment. It is a graph which shows a relationship. (A) is a longitudinal sectional view showing a state of horizontal deformation in the vicinity of the origin position of the weight in FIG. 2, and (b) is a graph showing the relationship between the weight deformation and the damping coefficient ratio α at that time. (A) is a longitudinal cross-sectional view which shows the state further deform | transformed horizontally from the position of the weight of FIG. 3, (b) is a graph which shows the relationship between the deformation | transformation of the weight in that case, and attenuation coefficient ratio (alpha). (A) is a longitudinal cross-sectional view which shows the state further deform | transformed further horizontally from the position of the weight of FIG. 4, (b) is a graph which shows the relationship between the deformation | transformation of the weight in that case, and attenuation coefficient ratio (alpha). It is the schematic which shows other embodiment of this invention. It is a front view which shows schematic structure of the conventional pendulum type TMD. It is a schematic diagram which shows the state which the weight of TMD of FIG.

1 to 5 show an embodiment of a vibration damping device according to the present invention, and parts that are the same as those shown in FIG.
As shown in FIG. 1, this vibration damping device 1 has a pendulum type TMD in which a weight 1 is suspended by a wire or a steel rod 2 as shown in FIG. 7, and is different from a conventional TMD. The point is that the weight 1 is provided with an oil damper 3 that suppresses vibration in the vertical direction.

  The oil damper 3 has one end 4 pin-coupled to the lower surface of the weight 1 and the other end 5 pin-coupled to the building 52 described above, so that the other end corresponds to the swing of the weight 1. The portion 5 is stretched and deformed while being tilted about the fulcrum.

The oil damper 3 is preferably set so that the damping coefficient of the oil damper 3 in a normal state (when there is no horizontal deformation of the weight 1) is C ₀ so that the damping coefficient increases as the deformation due to the expansion / contraction increases. Then, in FIG. 1, when the weight 1 swings during an earthquake and the inclination angle of the oil damper 3 with respect to the vertical line is θ, the damping coefficient C is set to be (C ₀ / cos ² θ). ing.

That is, in FIG. 1, when the suspended length of the weight 1 is L ₁ , the length when the oil damper 3 is installed is L ₂ , and the horizontal deformation of the weight 1 is δ _h ,
Deformation of the weight in the vertical direction: δ _v = L ₁ − (L ₁ ² −δ _h ² ) ^1/2
Deformation of oil damper: δ _oil = {δ _h ² + (L ₂ + δ _v ) ² } ^1/2 −L ₂
Oil damper angle: cos θ = (L ₂ + δ _v ) / {δ _h ² + (L ₂ + δ _v ) ² } ^1/2
Damping coefficient of oil damper: C = α ・ C ₀ = C ₀ / cos ² θ
Oil damper vertical damping coefficient: C _v = α _v · C ₀ = C ₀ · cos ² θ = C ₀ (constant)
Oil damper horizontal damping coefficient: C _h = α _h · C ₀ = C · sin ² θ = C ₀ · tan ² θ

2 (a) is the length of time of installing the hanging length of the weight 1 in L ₁ and the oil damper 3 for L _2, L ₁ = 4m, when the L ₂ = 1 m and L ₁ = 6 m, L ₂ The relationship between the deformation δ _oil of the oil damper and the damping coefficient ratio α in the case of = 1 m is shown. From the figure, as the deformation of the oil damper 3 increases, the damping coefficient C of the oil damper 3 increases.

Further, FIG. 2B shows the horizontal deformation δ _h of the weight 1 and the vertical damping coefficient C _v of the oil damper 3 when L ₁ = 4 m and L ₂ = 1 m are divided by the damping coefficient C ₀ . The relationship between the damping coefficient ratio α _v and the damping coefficient ratio α _h obtained by dividing the horizontal damping coefficient _Ch by the damping coefficient C ₀ is shown.

As seen in FIG. 2B, the vertical attenuation coefficient ratio α _v is 1.0 regardless of the horizontal deformation of the weight 1, whereas the horizontal attenuation coefficient _Ch is As the horizontal deformation of the weight 1 increases, its value increases.

3 to 5 show a specific configuration of the oil damper 3 in which the damping coefficient increases as the deformation increases.
In these drawings, the oil damper 3 has a piston 11 movably provided in a cylinder 10 filled with oil (working fluid), and a rod 12 integrated with the piston 11 is connected to the building 52 side. At the same time, the cylinder 10 is connected to the weight 1 of the TMD.

  Here, the cylinder 10 is provided with a bypass pipe 13 for communicating the inside of the cylinder 10 before and after the piston 11, and a shut-off valve 14 is interposed in the bypass pipe 13. The shut-off valve 14 is formed with a small-diameter portion 14 a that allows the bypass pipe 13 to communicate with the upper portion, and a large-diameter portion 14 b that is substantially equal to the inner diameter of the bypass pipe 13 is formed in the other portion.

  The shutoff valve 14 is urged by a spring 15 interposed between the shutoff valve 14 and the outer surface of the cylinder 10 so that the small diameter portion 13a is positioned in the bypass pipe 13 in a normal state. On the other hand, an arm 16 for integrally controlling the shutoff valve 14 is integrally formed on the rod 12 of the piston 11.

  The arm 16 is formed in parallel with the axis of the cylinder 10, and a displacement detection groove 17 is formed on the surface 16 a of the arm 16 facing the cylinder 10 so that the tip of the shutoff valve 14 abuts. The displacement detection groove 17 has an inclined surface in which the central portion 17a in the axial direction has the largest depth dimension, and the depth dimension gradually decreases from the central portion 17a toward the front side and the rear side in the axial direction. 17b.

  And this displacement detection groove | channel 17 is formed in the position where the front-end | tip part of the shutoff valve 14 contact | abuts to the center part 17a in normal times.

  In the oil damper 3, as shown in FIG. 3, when a slight sway is generated due to a normal condition or wind, the movement of the piston 11 with respect to the cylinder 10 is small because the sway of the weight 1 is slight. . As a result, since the shut-off valve 14 is positioned at the central portion 17a of the displacement detection groove 17 and the small-diameter portion 14a is disposed in the bypass pipe 13, the oil in the cylinder 10 is reciprocated when the piston 11 reciprocates small. Flows through the hole formed in the piston 11 and the bypass pipe 13 to generate a small damping force.

  As shown in FIG. 4, when the weight 1 is swung during the earthquake and the oil damper 3 is moderately deformed, the shutoff valve 14 is moved in the displacement detection groove 17 by the relative displacement between the cylinder 10 and the arm 16. It moves on the inclined surface 17b. Then, a part of the bypass pipe 13 is blocked by the large-diameter portion 14b of the shutoff valve 14, and the oil flow rate is reduced, so that a larger damping force than the state shown in FIG. 3 is generated.

  As shown in FIG. 5, when the weight 1 further swings greatly, the shutoff valve 14 rides on the surface 16 a of the arm 16 due to a large relative displacement generated between the cylinder 10 and the arm 16, and as a result, the bypass pipe 13. 4 is completely blocked by the large-diameter portion 14b of the shut-off valve 14, thereby generating a damping force that is much greater than that shown in FIG.

  As described above, according to the vibration damping device having the above-described configuration, when the swing of the TMD weight 1 increases and the deformation of the oil damper 3 increases during an earthquake, the damping coefficient of the oil damper 3 gradually increases. Therefore, the decrease in the vertical component of the damping force of the oil damper 3 due to the inclination of the weight 1 in the horizontal direction as it moves away from the origin position (vertical position) can be offset.

  As a result, according to the vibration damping device, even if the swing of the pendulum type TMD weight 1 increases during a large earthquake, the lifting of the weight 1 can be effectively suppressed.

FIG. 6 shows another embodiment of the present invention, and the same components as those shown in FIG. 1 are denoted by the same reference numerals.
In this vibration damping device, a recess 20 having a conical inner wall is formed at the bottom of the weight 1. The one end 4 of the oil damper 3 is pin-coupled to the top of the recess 20.

According to the vibration damping device having the above configuration, in addition to being able to obtain the same operational effects as those shown in FIGS. 1 to 5, the conical concave portion 20 is formed at the bottom of the weight 1. Since one end 4 of the oil damper 3 is pin-coupled to the top of the recess 20, the inclination angle θ ₁ of the oil damper 3 is set to the bottom of the weight 1 when the weight 1 swings δ _{h in the} horizontal direction during an earthquake. It is possible to make the inclination angle θ smaller than the case where the pin is coupled to.

  As a result, compared to the case where the oil damper 3 is pin-coupled to the bottom of the weight 1, the vertical component of the damping force in the oil damper 3 can be increased, and thus the damping coefficient increases as the deformation increases. In combination with this, the lifting of the weight 1 can be more effectively suppressed.

  In addition, in the said embodiment, although demonstrated about the case where a thing was used for a pendulum type as TMD, this invention is not limited to this. In other words, even in linear motion type (linear slider) type TMD and laminated rubber type TMD in which weights are placed on laminated rubber, if the weights are not constrained in the vertical direction, they move horizontally during an earthquake. At the same time, there is a possibility that it will resonate with the natural frequency in the vertical direction and float. For this reason, even when applied to these direct acting and laminated rubber type TMDs, the same effects can be obtained.

1 Weight 2 Wire or steel bar 3 Oil damper (damper)
4 One end 5 Other end 20 Recess

Claims (3)

  A damper having one end connected to the weight of the TMD and the other end connected to the structure and deformed in the vertical direction by the swing of the weight, and the damping coefficient increases as the deformation increases. A vibration damping device characterized by being provided.   The damper is an oil damper, and a shut-off valve that narrows the flow path of the bypass pipe as the deformation between the weight and the bypass pipe communicating with the front and rear of the piston in the cylinder filled with the working fluid increases. The vibration damping device according to claim 1, wherein:   2. The TMD is a pendulum type, and a concave portion having an inner wall conical surface is formed at a bottom portion of the weight, and an end portion of the damper is connected to a top portion of the concave portion. Or the damping device of 2.

Images