JP2016038049A - Vibration control system - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vibration control system facilitating adjustment of a cycle without using an inverted pendulum.SOLUTION: A vibration control system includes: an upper structure part fixed to a vibration control object; a first mass body suspended from the upper structure part; a lower structure part fixed to vibration control object; a second mass body supported to the lower structure part in a slidable manner in a horizontal direction; and a connection member constraining relative displacement in the horizontal direction between the first mass body and the second mass body while allowing relative displacement in a vertical direction between the first mass body and the second mass body.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a vibration suppression system.

  2. Description of the Related Art Conventionally, a pendulum type damping system including a mass body suspended from an upper structure portion is known. In Patent Documents 1 to 3, a pendulum composed of a mass body (first mass body) suspended from an upper structure part, and an inverted pendulum composed of a mass body (second mass body) supported upside down from a lower structure part; The vibration control system which connected and comprised was described.

JP 2011-12745 A JP 2012-141005 A JP-A-11-37212

  Since the inverted pendulum is unstable, it is not easy to install. In addition, the structure of the vibration suppression system becomes complicated when it is attempted to ensure the safety of the mass inverted pendulum.

  An object of this invention is to provide the damping system of the new structure which does not use an inverted pendulum.

  To achieve this object, the present invention provides an upper structure portion fixed to a vibration control object, a first mass suspended from the upper structure portion, and a lower structure section fixed to the vibration control object. And the second mass supported on the lower structure portion so as to be slidable in the horizontal direction, and the first mass while permitting relative displacement in the vertical direction between the first mass and the second mass. A vibration damping system comprising: a connecting member that restrains a relative displacement in a horizontal direction between a body and the second mass body.

  ADVANTAGE OF THE INVENTION According to this invention, the damping system of a new structure which does not use an inverted pendulum can be provided.

FIG. 1A is a diagram of the vibration damping system 1 according to the first embodiment viewed from above. FIG. 1B is a top view of the upper structure portion 11 omitted in FIG. 1A. 2A to 2C are cross-sectional explanatory views of each part of FIG. 1A. FIG. 3A is a model explanatory diagram of the first mass body M1 and the second mass body M2 of the vibration damping system 1 of the first embodiment. FIG. 3B is an explanatory diagram of horizontal and vertical displacements of the first mass body M1. 4A and 4B are operation explanatory views of the damper 32 of the vibration damping system 1 of the first embodiment. 5A to 5D are graphs of changes over time of the vibration damping system 1 of the first embodiment. FIG. 5E is a graph of the time change of the damping system 1 of the second embodiment, and is a graph of the time change of the damping force F when the damper 32 of FIG. 6B is used. FIG. 6A is a graph (FV diagram) of the damping force F of the damper 32 having a large damping coefficient C when the stroke changing speed V is small and a small damping coefficient C when the vertical stroke changing speed V is large. is there. FIG. 6B is a graph (CV diagram) of the damping coefficient C of the damper 32 having a large damping coefficient C when the stroke change speed V is small and a small damping coefficient C when the vertical stroke changing speed V is large. is there. 7A to 7C are graphs of the damping force F of the damper 32 with respect to the horizontal displacement Dx of the vibration damping system 1. FIG. 7A is a graph of the second reference example, FIG. 7B is a graph of the first embodiment, and FIG. 7C is a graph of the second embodiment. 8A and 8B are graphs of the damping force F of another damper 32. FIG. FIG. 9 is an explanatory diagram of the vibration damping system 1 of the third embodiment. FIG. 10A is a model explanatory diagram of the vibration damping system 1 of the first reference example. FIG. 10B is a model explanatory diagram of the vibration damping system 1 of the second reference example. 11A and 11B are explanatory diagrams of the operation of the damper 32 of the vibration damping system 1 of the second reference example of FIG. 10B. FIG. 12 is a graph of the damping force F of the damper 32 having a constant damping coefficient C. 13A to 13D are graphs of changes over time in the case of the second reference example. FIG. 14 is an explanatory diagram of a model of the vibration damping system 1 of the third reference example.

  At least the following matters will be apparent from the description and drawings described below.

  An upper structure fixed to the vibration control object, a first mass suspended from the upper structure, a lower structure fixed to the vibration control object, and the lower structure slidable in the horizontal direction The horizontal direction of the first mass body and the second mass body while allowing relative displacement in the vertical direction between the second mass body supported on the part and the first mass body and the second mass body. And a coupling member that restrains the relative displacement of the vibration damping system. Thereby, it is possible to realize a vibration suppression system that does not use an inverted pendulum.

  It is desirable to provide a damper disposed in the vertical direction between the first mass body and the second mass body. Thereby, a small stroke damper can be used.

  It is preferable that the damper has a large damping coefficient when the vertical relative speed between the first mass body and the second mass body is small, and the damping coefficient becomes small when the relative speed is large. Thereby, when the amplitude of the vibration control object is small, it is possible to suppress the absorption energy of the damper from being extremely reduced.

  It is desirable that the connecting member generates a restoring force with respect to a vertical relative displacement between the first mass body and the second mass body. Thereby, the excessive displacement of a 1st mass body and a 2nd mass body can be suppressed.

  It is desirable that the connecting member generates a damping force with respect to the relative movement in the vertical direction between the first mass body and the second mass body. Thereby, a damper is omissible.

  The first mass body preferably surrounds the second mass body. Alternatively, it is preferable that the second mass body surrounds the first mass body. When the second mass body surrounds the first mass body, the interval between the suspension members can be reduced.

=== Reference Example ===
<First Reference Example>
FIG. 10A is a model explanatory diagram of the vibration damping system 1 of the first reference example. The vibration suppression system 1 of the first reference example is a pendulum type vibration suppression system 1 configured of a mass body M suspended from an upper structure portion 11.

  If the length of the suspension member 21 that suspends the mass body M is L, the period T of the mass body M of the first reference example is as follows.

  T = 2π√ (L / g)

  That is, in the case of the vibration damping system 1 of the first reference example, the period T depends only on the length L of the suspension member 21. For this reason, when the natural period of the building to be controlled is long, in the vibration suppression system 1 of the first reference example, it is necessary to increase the length L of the suspension member 21, which increases the size of the vibration suppression system 1. End up.

  In addition, when adjusting the period T of the vibration damping system 1, there is no choice but to adjust the length L of the suspension member 21. However, since the mass body M has a large mass, it takes time and cost to adjust the length L of the suspension member 21 while ensuring safety.

<Second Reference Example>
FIG. 10B is a model explanatory diagram of the vibration damping system 1 of the second reference example. The vibration suppression system 1 of the second reference example has a structure in which a damper 32 is further added to the vibration suppression system 1 of the first reference example.
The damper 32 of the second reference example is arranged so as to generate a damping force with respect to the horizontal displacement of the mass body M. However, since the length L of the suspension member 21 needs to be increased when the natural period of the building that is the vibration suppression object is long, the displacement of the mass body M in the horizontal direction increases as a result. For this reason, the damper 32 of the second reference example needs to follow the mass body M that is largely displaced in the horizontal direction. However, the damper 32 having a large stroke (for example, a stroke of several meters) is expensive.

<Third reference example>
FIG. 14 is an explanatory diagram of a model of the vibration damping system 1 of the third reference example.
The vibration damping system 1 of the third reference example is configured by connecting a pendulum formed by the first mass body M1 and the suspension member 21 and an inverted pendulum formed by the second mass body M2 and the support arm 22 by a connecting member 31. In addition, in order to stabilize the vibration of the 1st mass body M1 and the 2nd mass body M2, the 2nd mass body M2 is comprised so that mass may become smaller than the 1st mass body M1. The connecting member 31 restrains the relative displacement in the horizontal direction between the first mass body M1 and the second mass body M2 while allowing the relative displacement in the vertical direction between the first mass body M1 and the second mass body M2.

  When the mass of the first mass body M1 is m1, the mass of the second mass body M2 is m2, and the lengths of the suspension member 21 and the support arm 22 are L, the period T of this model is as follows: As described above, since the second mass body M2 has a smaller mass than the first mass body M1, m1-m2> 0.

  T = 2π√ {(L / g) × (m1 + m2) / (m1−m2)}

In the case of the vibration damping system 1 of the third reference example, the period T depends not only on the length L of the suspension member 21 but also on the masses of the first mass body M1 and the second mass body M2. For this reason, if the mass of the 1st mass body M1 and the 2nd mass body M2 is adjusted, the length L of the suspension member 21 can be shortened. Further, if the masses of the first mass body M1 and the second mass body M2 are adjusted, the period T can be adjusted without adjusting the length L of the suspension member 21 or the like.
However, since the inverted pendulum (the second mass body M2 and the support arm 22) is unstable alone, the installation work of the vibration damping system 1 of the third reference example is not easy. Further, since the second mass body M2 has a large mass, the structure of the vibration damping system 1 becomes complicated when it is attempted to ensure the safety of the unstable inverted pendulum.

=== First Embodiment ===
<Basic configuration>
FIG. 1A is a diagram of the vibration damping system 1 according to the first embodiment viewed from above. FIG. 1B is a top view of the upper structure portion 11 omitted in FIG. 1A. 2A to 2C are cross-sectional explanatory views of each part of FIG. 1A.

  The vibration damping system 1 of the first embodiment includes an upper structure portion 11, a lower structure portion 12, a first mass body M1, a suspension member 21, a second mass body M2, a connection member 31, and a damper 32. Have

  The upper structure part 11 and the lower structure part 12 are structure parts fixed to a building that is a vibration control object. The lower structure part 12 is, for example, a floor of a building, and the upper structure part 11 is, for example, a steel frame fixed to the floor.

  The first mass body M <b> 1 is a mass body suspended from the upper structure portion 11 by the suspension member 21. The suspension member 21 is a member that suspends the first mass body M1 from the upper structure portion 11. The upper end of the suspension member 21 is rotatably connected to the upper structure portion 11, and the lower end is rotatably connected to the first mass body M <b> 1. The first mass body M1 and the suspension member 21 constitute a pendulum.

  The second mass body M2 is a mass body supported so as to be slidable in the horizontal direction with respect to the lower structure portion 12. The second mass body M2 is supported on the lower structure portion 12 by a support member 23 such as a rolling support so as to be slidable in the horizontal direction. The support member 23 is a support member that supports the second mass body M2 on the lower structure portion 12 so as to be slidable in the horizontal direction.

  In 1st Embodiment, since the 2nd mass body M2 is directly supported by the lower structure part 12, the support arm 22 of a 3rd reference example becomes unnecessary, and it is 2nd compared with installation of an unstable inverted pendulum. Installation of the mass body M2 becomes easy.

The connecting member 31 is a member that connects the first mass body M1 and the second mass body M2. The connecting member 31 restrains the relative displacement in the horizontal direction between the first mass body M1 and the second mass body M2. Thereby, the displacement of the horizontal direction of the 1st mass body M1 and the 2nd mass body M2 becomes the same. When the first mass body M1 and the second mass body M2 are displaced in the horizontal direction, the first mass body M1 is displaced upward in the vertical direction, so that the connecting member 31 is connected to the first mass body M1 and the second mass body M2. The relative displacement in the horizontal direction between the first mass body M1 and the second mass body M2 is restrained while allowing the relative displacement in the vertical direction. In the first embodiment, the second mass body M2 is not displaced in the vertical direction.
Here, laminated rubber is used as the connecting member 31. However, the connecting member 31 is not limited to the laminated rubber, and the first mass M1 and the second mass M2 are allowed while allowing the relative displacement in the vertical direction between the first mass M1 and the second mass M2. Other members may be used as long as they are members that restrain the relative displacement in the horizontal direction. For example, the connecting member 31 may have a damping function such as a natural rubber (LRB) containing a lead plug or a high damping laminated rubber. In this case, the damper 32 can be omitted. The connecting member 31 may be a rolling type like a linear slider.

  When laminated rubber is used for the connecting member 31, the laminated rubber functions like a spring, and the vertical resistance force (restoration) against the vertical relative displacement between the first mass body M1 and the second mass body M2. Force). When the amount of movement in the horizontal direction of the first mass body M1 and the second mass body M2 is small, the relative displacement between the first mass body M1 and the second mass body M2 is small, so the resistance force of the spring is small. When the amount of movement of the mass body M1 and the second mass body M2 in the horizontal direction is large, the relative displacement between the first mass body M1 and the second mass body M2 increases, and the resistance force of the spring increases. For this reason, when the connection member 31 that functions as a spring is employed like a laminated rubber, excessive displacement of the first mass body M1 and the second mass body M2 can be suppressed, and the vibration damping system having a fail-safe function. 1 is effective.

The damper 32 is arranged in the vertical direction between the first mass body M1 and the second mass body M2. When the relative displacement in the vertical direction between the first mass body M1 and the second mass body M2 changes, the stroke of the damper 32 expands and contracts. Thereby, the damper 32 generates a damping force with respect to the relative velocity in the vertical direction between the first mass body M1 and the second mass body M2. Even if the first mass body M1 and the second mass body M2 are largely displaced in the horizontal direction, the relative displacement in the vertical direction between the first mass body M1 and the second mass body M2 is small, and therefore a small stroke damper 32 is used. Therefore, the vibration damping system 1 becomes inexpensive.
Here, an oil damper is used as the damper 32. However, the damper 32 is not limited to the oil damper, and may be a damping top (RDT) or the like.

FIG. 3A is a model explanatory diagram of the first mass body M1 and the second mass body M2 of the vibration damping system 1 of the first embodiment.
When the mass of the first mass body M1 is m1, the mass of the second mass body M2 is m2, and the length of the suspension member 21 is L, the period T of this model is as follows.

  T = 2π√ {(L / g) × (m1 + m2) / m1}

  That is, in the case of the vibration damping system 1 of the first embodiment, the period T is not only the length L of the suspension member 21 but also the masses of the first mass body M1 and the second mass body M2 as in the third reference example. Also depends on. For this reason, if the mass of the 1st mass body M1 and the 2nd mass body M2 is adjusted, the length L of the suspension member 21 can be shortened, the height of the damping system 1 is suppressed, and the damping system 1 is small. Can be achieved. Further, if the masses of the first mass body M1 and the second mass body M2 are adjusted, the period T can be adjusted without adjusting the length L of the suspension member 21, so that the adjustment work is facilitated. .

  In the first embodiment, since the second mass body M2 is not displaced in the vertical direction, the relative displacement in the vertical direction between the first mass body M1 and the second mass body M2 is smaller than that in the third reference example. If a damper is disposed between the first mass body M1 and the second mass body M2 of the third reference example, the length L of the suspension member 21 and the support arm 22 is 3 m, and the first mass body M1 and If the horizontal displacement of the second mass M2 is 2 m, the stroke of the damper 32 is about 160 cm (± 80 cm). On the other hand, in the first embodiment, when the length L of the suspension member 21 is 3 m and the horizontal displacement of the first mass body M1 and the second mass body M2 is 2 m, the stroke of the damper 32 is about 80 cm. (± 40 cm). As described above, the damper 32 of the first embodiment can have a small stroke.

=== Second Embodiment ===
<Reference explanation 1: Damping force of the damper of the second reference example>
11A and 11B are explanatory diagrams of the operation of the damper 32 of the vibration damping system 1 of the second reference example of FIG. 10B. FIG. 11A is an explanatory diagram of the horizontal displacement Dx of the vibration damping system 1. In the following description, the horizontal displacement of the vibration damping system 1 due to the vibration of the vibration damping object is assumed to be Dx. FIG. 11B is an explanatory diagram of the operation of the damper 32 of the second reference example of FIG. 10B. Here, the horizontal stroke amount of the damper 32 is dx, the changing speed of the horizontal stroke of the damper 32 is Vx, and the damping force (resistance force) of the damper 32 is F.

  FIG. 12 is a graph of the damping force F of the damper 32 having a constant damping coefficient C. The horizontal axis of the graph indicates the stroke change speed V of the damper 32, and the vertical axis of the graph indicates the damping force F (resistance force). The damping force F is a product of the damping coefficient C and the velocity V (F = C × V). In other words, the slope of the graph of FIG. 12 is the attenuation coefficient C, and here the slope of the graph is constant (the attenuation coefficient C is constant).

  13A to 13D are graphs of changes over time in the case of the second reference example. FIG. 13A is a graph of the time change of the horizontal displacement Dx of the vibration suppression system 1. FIG. 13B is a graph of the time change of the stroke amount dx in the horizontal direction of the damper 32. In the case of the second reference example, the horizontal stroke amount dx of the damper 32 matches the horizontal displacement Dx of the vibration damping system 1. FIG. 13C is a graph of the time change of the stroke change speed Vx in the horizontal direction of the damper 32. The horizontal stroke change speed Vx of the damper 32 is the first derivative of the horizontal stroke amount dx of the damper 32. FIG. 13D is a graph of the time change of the damping force F of the damper 32 of the second reference example. The damping force F in FIG. 13D can be calculated as the product of the velocity Vx in FIG. 13C and a constant damping coefficient C (the slope of the graph in FIG. 12).

  FIG. 7A is a graph of the damping force F of the damper 32 with respect to the horizontal displacement Dx of the vibration damping system 1 of the second reference example. As shown in the figure, in the vibration damping system 1 of the second reference example, a predetermined damping force F can be obtained even when the horizontal displacement Dx is near zero. Further, even when the amplitude of the vibration control object is small, a damping force F corresponding to the horizontal displacement Dx can be obtained (however, as described above, the damper 32 of the second reference example has a large stroke, There will be a cost).

<Reference explanation 2: When the damping coefficient C of the damper 32 of the first embodiment is constant>
FIG. 3B is an explanatory diagram of horizontal and vertical displacements of the first mass body M1. When the first mass body M1 is displaced in the horizontal direction, the first mass body M1 is also displaced in the vertical direction. At this time, the relative displacement in the vertical direction has a non-linear relationship with respect to the displacement in the horizontal direction. Further, the change in the stroke of the damper 32 arranged in the vertical direction between the first mass body M1 and the second mass body M2 is also caused by the horizontal displacement of the first mass body M1 and the second mass body M2. Non-linear relationship. As a result, even if the first mass body M1 and the second mass body M2 are displaced in the horizontal direction, the relative displacement in the vertical direction of the first mass body M1 and the second mass body M2 hardly changes and the damper 32 is attenuated. There may be little force.

  4A and 4B are operation explanatory views of the damper 32 of the vibration damping system 1 of the first embodiment. Similarly to the above, as shown in FIG. 4A, the horizontal displacement of the vibration damping system 1 due to the vibration of the vibration damping object is defined as Dx. FIG. 4B is an explanatory diagram of the operation of the damper 32 of the first embodiment. Here, the vertical stroke amount of the damper 32 is dz, the change rate of the vertical stroke of the damper 32 is Vz, and the damping force (resistance force) of the damper 32 is F. The vertical stroke amount dz of the damper 32 becomes maximum when the first mass body M1 and the second mass body M2 are at the reference position, and the first mass body M1 and the second mass body M2 are maximum in the horizontal direction. Minimum when displaced. The vertical stroke change speed Vz of the damper 32 corresponds to the vertical relative speed of the first mass body M1 and the second mass body M2.

5A to 5D are graphs of changes over time of the vibration damping system 1 of the first embodiment. FIG. 5A is a graph of the time change of the horizontal displacement Dx of the vibration damping system 1.
FIG. 5B is a graph of the time change of the stroke amount dz in the vertical direction of the damper 32. In the second reference example described above, the horizontal stroke amount dx of the damper 32 coincides with the horizontal displacement Dx of the vibration damping system 1, whereas the vertical stroke amount dz ( FIG. 5B) has a non-linear relationship with respect to the horizontal displacement Dx (FIG. 5A) of the vibration suppression system 1. This is because, in the second reference example, the damper 32 is arranged in the horizontal direction, whereas the damper 32 of the first embodiment is arranged in the vertical direction.
FIG. 5C is a graph of the change over time of the stroke change speed Vz in the vertical direction of the damper 32. The vertical stroke change speed Vz of the damper 32 is a first derivative of the stroke amount dz of the damper 32 in the vertical direction. The vertical stroke change speed Vz of the damper 32 corresponds to the vertical relative speed of the first mass body M1 and the second mass body M2. FIG. 5D is a graph of the time change of the damping force F of the damper 32. Here, the damping coefficient C of the damper 32 is constant, and the damping force F in FIG. 5D can be calculated as the product of the velocity Vz in FIG. 5C and the constant damping coefficient C (the slope of the graph in FIG. 12).

  FIG. 7B is a graph of the damping force F of the damper 32 with respect to the horizontal displacement Dx of the vibration damping system 1 of the first embodiment when the damping coefficient C of the damper 32 is constant. As shown in the figure, in the first embodiment, the damping force F is hardly obtained when the horizontal displacement Dx is near zero. Further, due to the fact that the vertical stroke amount dz of the damper 32 is non-linear with respect to the horizontal displacement Dx of the vibration damping system 1, the damping force F of the damper 32 is dependent on the amplitude, and the horizontal displacement Dx is small. As a result, when the amplitude of the damping object is reduced, the absorbed energy of the damper 32 is extremely reduced (as compared to the case of FIG. 7A, the damping force F is significantly reduced). . Thus, if the absorption energy of the damper 32 with respect to amplitude changes extremely, the problem that it becomes difficult for the damping system 1 to obtain the damping force F according to amplitude will arise.

  For this reason, it is desirable that the absorbed energy of the damper 32 is not extremely reduced even when the amplitude of the vibration control object is reduced. Therefore, in the second embodiment, the damping force F during the initial operation of the damper 32 is secured by using the damper 32 having the characteristics described below.

Second Embodiment
FIG. 6A is a graph (FV diagram) of the damping force F of the damper 32 having a large damping coefficient C when the stroke changing speed V is small and a small damping coefficient C when the vertical stroke changing speed V is large. is there. The horizontal axis of the graph in FIG. 6A indicates the stroke change speed V of the damper 32, and the vertical axis of the graph indicates the damping force F (resistance force). Here, the damping force F increases in proportion to the changing speed V in the low speed region of the changing speed V (the region where the changing speed V is equal to or less than V1), and when the changing speed V exceeds V1, the damping force F becomes constant. ing.
FIG. 6B is a graph (CV diagram) of the damping coefficient C of the damper 32 having a large damping coefficient C when the stroke change speed V is small and a small damping coefficient C when the vertical stroke changing speed V is large. is there. The horizontal axis of the graph of FIG. 6B indicates the change speed V of the stroke of the damper 32, and the vertical axis of the graph indicates the attenuation coefficient C. Since the damping force F is the product of the damping coefficient C and the velocity V (F = C × V), the slope of the line connecting each point and the origin of the graph (FV diagram) in FIG. The damping coefficient C of the damper 32 is obtained. As shown in FIG. 6B, the damping coefficient C of the damper 32 becomes a constant value C1 in the low speed region of the change speed V (region where the change speed V is V1 or less), and increases when the change speed V exceeds V1. It has the characteristic which decreases with. For this reason, the damping coefficient C is large when the stroke change speed V of the damper 32 is small, and the damping coefficient C is small when the stroke change speed V is large. Since the damper 32 is disposed in the vertical direction between the first mass body M1 and the second mass body M2, the damper 32 is a relative velocity in the vertical direction between the first mass body M1 and the second mass body M2. Is small, and the damping coefficient C is small when the vertical relative velocity between the first mass body M1 and the second mass body M2 is large.

FIG. 5E is a graph of the time change of the damping force F when the damper 32 of FIG. 6B is used. The damping force F in FIG. 5E can be calculated as the product of the change speed Vz in FIG. 5C and the damping coefficient C (see FIG. 6B).
FIG. 7C is a graph of the damping force F of the damper 32 with respect to the horizontal displacement Dx of the vibration damping system 1 when the damper 32 (see FIGS. 6A and 6B) of the second embodiment is used. Although the damping force F is hardly obtained when the horizontal displacement Dx is near zero, compared with the case where the damping coefficient C of the damper 32 is constant (see FIG. 7B), even if the amplitude of the vibration control object is reduced, A damping force F is ensured. This is because the attenuation coefficient C is large when the vertical change rate Vz is small. Thereby, compared with the case where the damping coefficient C of the damper 32 is constant, even if the amplitude of the vibration control object is small, an extreme decrease in the absorbed energy of the damper 32 can be suppressed, and the damping force F corresponding to the amplitude can be easily obtained. Become.

  The damper 32 is not limited to the damper 32 having the characteristics shown in FIGS. 6A and 6B. FIG. 8A is a graph of the damping force F and damping coefficient C of another damper 32. The damper damping coefficient C (right graph in FIG. 8A) is the slope of the line connecting the points and the origin of the left graph in FIG. 8A. The damper 32 also has a large attenuation coefficient C when the vertical change speed Vz is small, and a small attenuation coefficient C when the vertical change speed Vz is large. Even when the damper 32 having such characteristics is used, the damping force F during the initial operation of the damper 32 is ensured, so that even if the amplitude of the vibration control object is small, the absorbed energy of the damper 32 is extremely reduced. Can be suppressed.

  In the damper 32 shown in FIGS. 6B and 8A, the damping coefficient C is constant in the low speed region of the change speed Vz. However, as shown in FIG. 8B, the damping coefficient C of the damper 32 may gradually decrease even in the low speed change region V (the slope of the line connecting each point of the left graph of FIG. 8B and the origin is It may be gradually reduced). Even when the damper 32 having such characteristics is used, the damping force F during the initial operation of the damper 32 is ensured, so that even if the amplitude of the vibration control object is small, the absorbed energy of the damper 32 is extremely reduced. Can be suppressed.

  As described above, when the connecting member 31 that functions as a spring like a laminated rubber is employed, excessive displacement of the first mass body M1 and the second mass body M2 due to the resistance force (restoring force) of the spring. Can be suppressed. For this reason, the damper 32 having a small damping coefficient C when the vertical stroke change speed V is large, and the resistance force (restoring force) of the spring with the increase in the horizontal displacement of the first mass body M1 and the second mass body M2. By using together with the connecting member 31 that becomes larger, it is possible to configure the damping system 1 that can exhibit the damping effect in a wide range from a low amplitude to a large amplitude while having a function of preventing excessive displacement of the mass body. Become.

=== Third Embodiment ===
In the first and second embodiments, the first mass body M1 surrounds the second mass body M2. However, the second mass body M2 may surround the first mass body M1.
FIG. 9 is an explanatory diagram of the vibration damping system 1 of the third embodiment. In the third embodiment, the second mass body M2 surrounds the first mass body M1. Thereby, since the 1st mass body M1 is located inside the 2nd mass body M2, the space | interval of the suspension member 21 can be narrowed. Accordingly, it is possible to further narrow the upper side of the internal space of the upper structure portion 1.

  Also in the third embodiment, it is preferable to use the damper 32 having the characteristics shown in FIGS. 6A and 6B. That is, the damping coefficient C when the stroke change speed V (the relative speed in the vertical direction between the first mass body M1 and the second mass body M2) is small is large, and the damping coefficient C when the stroke speed V in the vertical direction is large. A small damper 32 may be used. Thereby, compared with the case where the damping coefficient C of the damper 32 is constant, even if the amplitude of the vibration control object is small, an extreme decrease in the absorbed energy of the damper 32 can be suppressed, and the damping force F corresponding to the amplitude can be easily obtained. Become.

  Note that the damper 32 disposed between the first mass body M1 and the second mass body M2 may be omitted. In this case, it is preferable to use a connecting member 31 having a damping function (restoring function) such as a lead laminated natural laminated rubber (LRB) or a high damping laminated rubber.

=== Other Embodiments ===
The above embodiment is for facilitating the understanding of the present invention, and is not intended to limit the present invention. The present invention can be changed and improved without departing from the gist thereof, and it is needless to say that the present invention includes equivalents thereof.

1 Damping system,
11 Superstructure part,
12 Substructure part,
21 suspension members,
22 support arms,
23 bearing members,
31 connecting member,
32 damper,
M1 first mass body,
M2 second mass

Claims (7)

A superstructure fixed to the object to be damped;
A first mass suspended from the upper structure,
A lower structure fixed to the vibration control object;
A second mass body supported on the lower structure portion so as to be slidable in a horizontal direction;
A connecting member that restrains the relative displacement in the horizontal direction between the first mass body and the second mass body while allowing the relative displacement in the vertical direction between the first mass body and the second mass body; Damping system characterized by The vibration damping system according to claim 1,
A vibration damping system comprising a damper disposed in the vertical direction between the first mass body and the second mass body. The vibration damping system according to claim 2,
The damper has a large damping coefficient when the vertical relative speed between the first mass body and the second mass body is small, and the damping coefficient becomes small when the relative speed is large. Vibration suppression system. The vibration damping system according to any one of claims 1 to 3,
The said connection member produces a restoring force with respect to the relative displacement of the perpendicular direction of a said 1st mass body and a said 2nd mass body, The damping system characterized by the above-mentioned. The vibration damping system according to claim 1,
The said damping member produces damping force with respect to the said vertical relative movement of the said 1st mass body and the said 2nd mass body, The damping system characterized by the above-mentioned. A vibration damping system according to any one of claims 1 to 5,
The damping system according to claim 1, wherein the first mass body surrounds the second mass body. A vibration damping system according to any one of claims 1 to 5,
The damping system according to claim 1, wherein the second mass body surrounds the first mass body.

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