JP5123623B2 - Seismic isolation devices and vibration control devices - Google Patents

Description

  The present invention relates to a seismic isolation device that isolates vibrations of a target structure or a damping device that suppresses vibrations. In particular, the present invention relates to a seismic isolation device that isolates vibration energy of a target structure that is shaken by an earthquake or the like, or a vibration suppression device that controls vibration.

When an earthquake occurs, target structures such as buildings and structures are shaken horizontally and vertically.
If the acceleration level due to an earthquake or the like is large, the target structure may be damaged, or an object in the target structure may receive an acceleration exceeding the expectation, or may be displaced beyond the expectation.
Therefore, the seismic isolation device that reduces the vibration energy transmitted from the foundation to the target structure or isolates the vibration, or absorbs the vibration energy when the target structure vibrates and reduces the vibration level to control the vibration. Devices having various structures have been tried as vibration damping devices.
By appropriately setting the specifications of the structure and the elements constituting the structure, desired seismic isolation performance and damping performance can be exhibited.

Japanese Patent Laid-Open No. 10-100955 JP-A-10-184757 JP 2000-017885 A JP 2003-138784 A JP 2004-239411 A JP 2005-180492 A JP 2005-207547 A

  However, it is not easy to appropriately set the structure for exhibiting the desired seismic isolation performance or damping performance and the specifications of the elements constituting the structure.

  The present invention has been devised in view of the above-described problems, and it is possible to easily set the specifications of a device capable of exhibiting a desired seismic isolation performance or damping performance with a simple structure and the elements constituting the device. Try to provide seismic isolation devices and vibration control devices.

  In order to achieve the above object, a seismic isolation device for isolating a displacement in a specific direction of a target structure supported by a main frame on the basis of a support according to the present invention, and a relative displacement in a specific direction as a rotation amount of a rotating body. An inertial connection element that converts to, a spring element that generates an elastic reaction force that acts along a specific direction corresponding to a relative displacement in a specific direction, and a specific direction that corresponds to a relative velocity in a specific direction A damper element for generating a damping resistance, and a viscous mass damper with a spring, which is a system in which the inertial connection element and the damper element are connected in parallel and the spring element in series, includes a support and a target structure. It was supposed to be connected between things.

With the above-described configuration of the present invention, the inertia connecting element converts the relative displacement in the specific direction into the rotation amount of the rotating body. The spring element generates an elastic reaction force acting along a specific direction corresponding to the relative displacement in the specific direction. The damper element generates a damping resistance that acts along a specific direction corresponding to a relative speed in the specific direction. A viscous mass damper with a spring which is a system in which the inertia connecting element and the damper element are connected in parallel and the spring element is connected in series is connected between the support and the target structure.
As a result, when the target structure vibrates in a specific direction, a vibration system composed of the inertia connecting element and the spring element vibrates, the inertia connecting element is relatively displaced, and the dampers connected in parallel The element displaces and absorbs vibration energy.

  Below, the seismic isolation apparatus which concerns on embodiment of this invention is demonstrated. The present invention includes any of the embodiments described below, or a combination of two or more of them.

The seismic isolation device according to the embodiment of the present invention includes a natural frequency ωr corresponding to an elastic coefficient kb of the spring element and an apparent inertial mass mr with respect to a relative acceleration in a specific direction of the inertia connecting element, a main frame, The ratio of the natural frequency ωn of the vibration mode displaced in a specific direction of the system composed of the target structure is adjusted, and the ratio ω / ωn between the excitation frequency ω and the natural frequency ωn is taken as the horizontal axis. When the response magnification of the structure is the vertical axis, it is constant regardless of the value of the damping coefficient c that is a value obtained by dividing the damping resistance force of the damper element by the relative speed on the line indicating the response magnification. The values at the two fixed points are substantially equal, and the response magnification is the target that vibrates in response to the static displacement of the target structure due to the excitation force when the target structure is forcibly excited. Absolute response magnification, which is the ratio to the amplitude of the structure, strong support Object that vibrates in response to the displacement response magnification, which is the ratio of the displacement of the support when it is vibrated and the displacement of the target structure that vibrates in response, or the acceleration of the support when the support is forced It is assumed that it is one of the acceleration response magnifications that is a ratio with the acceleration of the object.
With the configuration of the embodiment according to the present invention, the natural frequency ωr corresponding to the elastic coefficient kb of the spring element and the apparent inertial mass mr with respect to the relative acceleration in a specific direction of the inertial connection element, the main frame, and the target structure The ratio of the natural frequency ωn of the vibration mode displaced in a specific direction of the system composed of the Is a constant value regardless of the value of the damping coefficient c, which is a value obtained by dividing the damping resistance force of the damper element by the relative speed on the line indicating the response magnification. The value at the fixed point should be approximately equal.
As a result, at a frequency in the vicinity of the excitation frequency ω corresponding to two fixed points, the response magnification determined by the elastic coefficient Kb of the spring element and the inertia mass mr of the inertia connecting element is substantially equal, and the damper element is The vibration energy can be absorbed along with the relative displacement along the specific direction of the inertial connection element, and the level of the vibration response of the target structure based on the support can be reduced.

Furthermore, in the seismic isolation device according to the embodiment of the present invention, the damping coefficient c is adjusted so that the values at the two fixed points are substantially substantially maximal.
With the configuration of the embodiment according to the present invention, the attenuation coefficient c is adjusted, and the values at the two fixed points are substantially substantially maximized respectively.
As a result, the damper element has an appropriate damping coefficient c, absorbs vibrational energy along with the relative displacement along a specific direction of the inertial connection element, and is used for absolute displacement of the target structure based on the support. The corresponding amplitude, relative displacement, or acceleration can be made smaller so that the vibration response level of the target structure based on the support does not exceed the response magnification corresponding to the two fixed points.

In the seismic isolation device according to the embodiment of the present invention, the elastic coefficient kb of the spring element is a value between 90% and 110% of k × (1-2μ-sqrt (1-4μ)) / 2μ. There,
A value between 90% and 110% of the damping coefficient c of the damper element is 2 × (31.095 μ ³ -12.04 μ ² +2.581 μ + 0.038) × ωr × mr, or
The elastic coefficient kb of the spring element is a value between 70% and 160% of k × (1-2μ + sqrt (1-4μ)) / 2μ,
The damping coefficient c of the damper element is 2 × (−18.558 μ ³ +4.880 μ ² −0.717 μ + 0.612) × ωr × mr between 70% and 160%. ,
here,
0 <μ ≦ 0.25,
μ = mr / m,
k is an elastic coefficient related to displacement along a specific direction of the main frame, m is a mass supported by the main frame of the target structure,
mr is the apparent inertial mass relative to the relative acceleration in a specific direction of the inertial connecting element;
kb is the elastic coefficient of the spring element,
ωr = sqrt (kb / mr),
sqrt (x) is the square root of x.
With the configuration of the above embodiment,
The elastic coefficient kb of the spring element is a value between 90% and 110% of k × (1-2μ-sqrt (1-4μ)) / 2μ;
The damping coefficient c of the damper element is a value between 90% and 110% of 2 × (31.095 μ ³ −12.041 μ ² +2.581 μ + 0.038) × ωr × mr.
Or
The elastic coefficient kb of the spring element is a value between 70% and 160% of k × (1-2μ + sqrt (1-4μ)) / 2μ,
The damping coefficient c of the damper element is a value between 70% and 160% of 2 × (−18.558 μ ³ +4.880 μ ² −0.717 μ + 0.612) × ωr × mr.
As a result, the system comprising the natural frequency ωr corresponding to the elastic coefficient kb of the spring element and the apparent inertial mass mr with respect to the relative acceleration in the specific direction of the inertia connecting element, the main frame, and the target structure is specified. When the ratio of the natural frequency ωn of the vibration mode displaced in the direction is adjusted, the ratio of the excitation frequency ω and the natural frequency ωn is the horizontal axis, and the displacement response magnification of the target structure is the vertical axis, On the line indicating the displacement response magnification, the values at the two fixed points that are constant regardless of the value of the damping coefficient c of the damper element are substantially equal, and the displacement response magnification is the value at one fixed point. Therefore, at a frequency in the vicinity of the excitation frequency ω corresponding to two fixed points, the displacement response magnification determined by the elastic coefficient Kb of the spring element and the inertia mass mr of the inertia connecting element becomes substantially equal, and the damper The element is The vibration energy can be absorbed with the relative displacement along the specific direction of the conductive connecting element, and the level of the vibration response of the target structure based on the support can be reduced.

In addition, the seismic isolation device according to the embodiment of the present invention,
The elastic coefficient kb of the spring element is a value between 90% and 110% of k × (2μ-1 + sqrt (1-2μ)) / (1-2μ),
The damping coefficient c of the damper element is a value between 90% and 110% of 2 × (4.436 μ ³ −3.619 μ ² +1.729 μ + 0.056) × ωr × mr,
here,
0 <μ ≦ 0.5,
μ = mr / m,
k is an elastic coefficient relating to displacement along a specific direction of the main frame,
m is the mass of the target structure,
mr is the apparent inertial mass relative to the relative acceleration in a specific direction of the inertial connecting element;
kb is the elastic coefficient of the spring element,
ωr = sqrt (kb / mr),
sqrt (x) is the square root of x,
It was supposed to be.
With the configuration of the above embodiment,
The elastic coefficient kb of the spring element is a value between 90% and 110% of k × (2μ-1 + sqrt (1-2μ)) / (1-2μ);
The damping coefficient c of the damper element is a value between 90% and 110% of 2 × (4.436 μ ³ −3.619 μ ² +1.729 μ + 0.056) × ωr × mr.
As a result, the system comprising the natural frequency ωr corresponding to the elastic coefficient kb of the spring element and the apparent inertial mass mr with respect to the relative acceleration in the specific direction of the inertia connecting element, the main frame, and the target structure is specified. Adjusting the ratio of the natural frequency ωn of the vibration mode displaced in the direction,
The value of the damping coefficient c of the damper element on the line indicating the acceleration response magnification, where the horizontal axis is the ratio of the excitation frequency ω and the natural frequency ωn and the acceleration response magnification of the target structure is the vertical axis. Because the values at the two fixed points, which are constant regardless of whether, are almost equal, and the acceleration response magnification does not exceed the values at the two fixed points,
At a frequency in the vicinity of the excitation frequency ω corresponding to two fixed points, the acceleration response magnification determined by the elastic coefficient Kb of the spring element and the inertial mass mr of the inertial connection element is substantially equal, and the damper element has the inertial force. Vibration energy is absorbed with relative displacement along a specific direction of the connecting element, and the level of vibration response of the target structure based on the support can be reduced.

  In order to achieve the above object, a seismic isolation device for isolating displacement in a specific direction of a target structure supported by a main frame on the basis of a support according to the present invention, a linear motion shaft provided with a male screw, and the male screw A viscous mass damper having a rotating body provided with a female screw that fits into the frame, a frame that rotatably supports the rotating body, an inner surface of the frame, and a viscous fluid sealed in a gap between the rotating body, an elastic body, A spring element having a first member and a second member sandwiched between the elastic bodies, wherein the linear motion direction of the linear motion shaft substantially coincides with the specific direction, and the frame or straight One of the dynamic shafts is connected to one of the support or the target structure, the other of the viscous mass damper frame or the linear motion shaft is connected to the first member of the spring element, and the second member of the spring element is supported. Connected to the other of the body or the target structure It was.

According to the configuration of the present invention, the viscous mass damper includes a linear motion shaft provided with a male screw, a rotating body provided with a female screw fitted to the male screw, a frame that rotatably supports the rotating body, an inner surface of the frame, and the A viscous fluid enclosed in a gap with the rotating body. The spring element includes an elastic body and a first member and a second member sandwiching the elastic body. A frame of the viscous mass damper is connected to one of the support and the target structure. The linear motion shaft of the viscous mass damper is connected to the first member of the spring element. The second member of the spring element is connected to the other of the support or the target structure.
As a result, when the target structure vibrates and moves in a specific direction, a vibration system composed of the viscous mass damper and the spring element vibrates, and the linear motion shaft relatively displaces in the linear motion direction and rotates. The body rotates, a shearing force is generated in the viscous fluid, and the viscous fluid absorbs vibration energy.

  Below, the seismic isolation apparatus which concerns on embodiment of this invention is demonstrated. The present invention includes any of the embodiments described below, or a combination of two or more of them.

The seismic isolation device according to an embodiment of the present invention includes an elastic coefficient kb that is a value obtained by dividing a reaction force generated when the spring element is displaced by a relative distance in the linear motion direction by the relative distance, and the viscous mass damper. When the linear motion shaft is linearly moved in the linear motion direction at a predetermined relative acceleration, the inherent inertia mass mr corresponding to the apparent inertial mass mr, which is a value obtained by dividing the reaction force acting in the linear motion direction by the relative acceleration. The ratio between the vibration frequency ωr and the natural frequency ωn of the vibration mode displaced in a specific direction of the system composed of the main frame and the target structure is adjusted, and the ratio ω / of the excitation frequency ω and the natural frequency ωn is adjusted. When ωn is the horizontal axis and the response magnification of the target structure is the vertical axis, the linear motion axis of the viscous mass damper is linearly moved at a constant relative speed on a line indicating the response magnification. Of the damping coefficient c, which is a value obtained by dividing the reaction force acting in the linear motion direction by the relative speed. The values at the two fixed points, which are constant regardless of whether or not, are substantially equal, and the response magnification is the static displacement of the target structure due to the excitation force when the target structure is forcibly excited. The absolute response magnification, which is the ratio of the amplitude of the target structure that vibrates in response, and the displacement that is the ratio of the displacement of the target structure that vibrates in response to the displacement of the support when the support is forcibly vibrated This is one of the response response rate or the acceleration response magnification which is a ratio between the acceleration of the support when the support is forcibly excited and the acceleration of the object that vibrates in response.
With the configuration of the above embodiment, the elastic coefficient kb, which is a value obtained by dividing the reaction force generated when the spring element is displaced by the relative distance in the linear motion direction, by the relative distance, and the linear motion shaft of the viscous mass damper. The natural frequency ωr corresponding to the apparent inertial mass mr, which is a value obtained by dividing the reaction force acting in the linear motion direction by the relative acceleration when the linear motion is linearly moved in the linear motion direction at a predetermined relative acceleration, The ratio of the natural frequency ωn of the vibration mode displaced in a specific direction of the system composed of the frame and the target structure is adjusted. When the horizontal axis represents the ratio of the excitation frequency ω and the natural frequency ωn, and the vertical axis represents one of the absolute response magnification, relative displacement response magnification, or acceleration response magnification of the target structure, the response The value of the damping coefficient c, which is a value obtained by dividing the reaction force acting in the linear motion direction by the relative velocity when the linear motion shaft of the viscous mass damper is linearly moved at a relative speed on a line indicating the magnification. Regardless of the time, the values at the two fixed points that are constant values are substantially equal.
As a result, at the frequency near the excitation frequency ω corresponding to two fixed points, the response magnification determined by the elastic coefficient Kb of the spring element and the inertia mass mr of the viscous mass damper becomes substantially equal, and the viscous mass The damper absorbs vibration energy with relative displacement between the frame and the linear motion shaft, and the vibration response level of the target structure based on the support can be reduced.

Furthermore, in the seismic isolation device according to the embodiment of the present invention, the damping coefficient c is adjusted so that the values at the two fixed points are substantially substantially maximal.
According to the configuration of the above embodiment, the attenuation coefficient c is adjusted, and the values at the two fixed points are substantially substantially maximized respectively.
As a result, the viscous mass damper has an appropriate damping coefficient c, absorbs vibration energy with the relative displacement of the frame and the direct coaxial, and corresponds to the absolute displacement of the target structure based on the support. The amplitude, relative displacement, or acceleration can be further reduced so that the vibration response level of the target structure based on the support does not exceed the response magnification corresponding to the two fixed points.

In order to achieve the above object, a damping device for damping vibrations with relative deformation in a specific direction of a target structure according to the present invention, an inertia connecting element that converts a relative displacement in a specific direction into a rotation amount of a rotating body, A spring element that generates an elastic reaction force that operates along a specific direction corresponding to a relative displacement in a specific direction, and a damper element that generates a damping resistance force that operates along a specific direction corresponding to a relative velocity in a specific direction When,
Between a pair of locations in which a viscous mass damper with a spring, which is a system in which the inertia connecting element and the damper element are connected in parallel, and a system in which the spring element is connected in series, is separated in a specific direction of the target structure. To be connected.

With the above-described configuration of the present invention, the inertial connection element converts the relative displacement in a specific direction into the rotation amount of the rotating body. The spring element generates an elastic reaction force acting along a specific direction corresponding to a relative displacement in the specific direction. The damper element generates a damping resistance force acting along a specific direction corresponding to a relative speed in the specific direction. A viscous mass damper with a spring which is a system in which the inertia connecting element and the damper element are connected in parallel and the spring element is connected in series is connected to a pair of locations spaced apart in a specific direction of the target structure.
As a result, when the target structure vibrates in a mode in which it moves relative to a specific direction, a vibration system composed of the inertia connecting element and the spring element vibrates, the relative displacement of the inertia connecting element, and parallel connection The formed damper element is relatively displaced to absorb vibration energy.

  Hereinafter, a vibration damping device according to an embodiment of the present invention will be described. The present invention includes any of the embodiments described below, or a combination of two or more of them.

  The vibration damping device according to the embodiment of the present invention specifies the natural frequency ωr corresponding to the elastic coefficient kb of the spring element and the apparent inertial mass mr with respect to the relative acceleration in the specific direction of the inertial connection element, and the target structure. When the ratio between the natural frequency ωn of the vibration mode displaced in the direction is adjusted, the ratio between the excitation frequency ω and the natural frequency ωn is taken as the horizontal axis, and the response magnification of the target structure is taken as the vertical axis, the response The values at two fixed points that are constant regardless of the value of the damping coefficient c, which is a value obtained by dividing the damping resistance of the damper element by the relative speed on the line indicating the magnification, are substantially equal. The response magnification is one of the target structures that vibrates in response to the static displacement of the one part of the target structure due to the excitation force when the one part of the target structure is forcibly vibrated. Absolute response magnification, which is the ratio of the amplitudes of Displacement response magnification, which is a ratio of the displacement of one of the locations when the one of the locations of the elephant structure is forcibly excited to the displacement of the other location of the target structure that vibrated in response, or the target structure Of the acceleration response magnification that is the ratio of the acceleration of one of the locations of the target structure and the acceleration of the other location of the target structure that vibrated in response to the forced excitation of one location of the object One.

According to the configuration of the above embodiment, the natural frequency ωr corresponding to the elastic coefficient kb of the spring element and the apparent inertial mass mr with respect to the relative acceleration in the specific direction of the inertial connection element and the vibration that is displaced in the specific direction of the target structure. The ratio of the mode to the natural frequency ωn is adjusted. When the horizontal axis represents the ratio of the excitation frequency ω and the natural frequency ωn, and the vertical axis represents one of the absolute response magnification, relative displacement response magnification, or acceleration response magnification of the target structure, the response On the line indicating the magnification, the values at the two fixed points that are constant regardless of the value of the damping coefficient c of the damper element are substantially equal.
As a result, at a frequency in the vicinity of the excitation frequency ω corresponding to two fixed points, the response magnification determined by the elastic coefficient Kb of the spring element and the inertia mass mr of the inertia connecting element is substantially equal, and the damper element is The vibration energy is absorbed in accordance with the relative displacement along the specific direction of the inertial connection element, and the level of the relative vibration response of the pair of locations separated in the specific direction of the target structure can be reduced.

Furthermore, in the vibration damping device according to the embodiment of the present invention, the damping coefficient c is adjusted so that the values at the two fixed points are substantially substantially maximized.
According to the configuration of the present invention, the attenuation coefficient c is adjusted, and the values at the two fixed points are substantially substantially maximized respectively.
As a result, the damper element has an appropriate damping coefficient c, absorbs vibration energy along with the relative displacement along a specific direction of the inertial connection element, and further increases the amplitude, relative displacement, or acceleration of the target structure. The relative vibration response level of a pair of locations that are separated in a specific direction of the target structure can be reduced so as not to exceed the response magnification corresponding to the two fixed points.

The vibration damping device according to the embodiment of the present invention is
The elastic coefficient kb of the spring element is a value between 90% and 110% of k × (1-2μ-sqrt (1-4μ)) / 2μ,
A value between 90% and 110% of the damping coefficient c of the damper element is 2 × (31.095 μ ³ -12.04 μ ² +2.581 μ + 0.038) × ωr × mr,
Or
The elastic coefficient kb of the spring element is a value between 70% and 160% of k × (1-2μ + sqrt (1-4μ)) / 2μ,
The damping element c has a value between 70% and 160% of 2 × (−18.558 μ ³ +4.880 μ ² −0.717 μ + 0.612) × ωr × mr,
It seems like
here,
0 <μ ≦ 0.25,
μ = mr / m,
ωr = sqrt (kb / mr)
k is an elastic coefficient of the spring when imitating vibration with relative deformation in a specific direction of the target structure in a one-mass system of spring and mass;
m is the mass of the mass point of the one mass system,
mr is the apparent inertial mass relative to the relative acceleration in a specific direction of the inertial connecting element;
kb is the elastic coefficient of the spring element,
sqrt (x) is the square root of x,
It was supposed to be.
With the configuration of the above embodiment,
The elastic coefficient kb of the spring element is a value between 90% and 110% of k × (1-2μ-sqrt (1-4μ)) / 2μ;
The damping coefficient c of the damper element is a value between 90% and 110% of 2 × (31.095 μ ³ −12.041 μ ² +2.581 μ + 0.038) × ωr × mr.
Or
The elastic coefficient kb of the spring element is a value between 70% and 160% of k × (1-2μ + sqrt (1-4μ)) / 2μ;
The damping coefficient c of the damper element is a value between 70% and 160% of 2 × (−18.558 μ ³ +4.880 μ ² −0.717 μ + 0.612) × ωr × mr.
As a result, the natural frequency ωr corresponding to the elastic coefficient kb of the spring element and the apparent inertial mass mr with respect to the relative acceleration in the specific direction of the inertial connection element and the natural vibration of the vibration mode displaced in the specific direction of the target structure. When the ratio between the excitation frequency ω and the natural frequency ωn is plotted on the horizontal axis and the displacement response magnification of the target structure is plotted on the vertical axis, the ratio to the number ωn is adjusted. Since the values at the two fixed points that are constant regardless of the value of the damping coefficient c of the damper element are substantially equal, the spring element at a frequency near the excitation frequency ω corresponding to the two fixed points. The displacement response magnification determined by the elastic coefficient Kb of the inertial connection element and the inertial mass mr of the inertial connection element are substantially equal, and the damper element absorbs vibration energy along with the displacement relative displacement along a specific direction of the inertial connection element. It is possible to reduce the relative vibration response level of a pair of locations that are separated and separated in a specific direction of the target structure.

The vibration damping device according to the embodiment of the present invention,
The elastic coefficient kb of the spring element is a value between 90% and 110% of k × (2μ-1 + sqrt (1-2μ)) / (1-2μ),
The damping coefficient c of the damper element is a value between 90% and 110% of 2 × (4.436 μ ³ −3.619 μ ² +1.729 μ + 0.056) × ωr × mr,
here,
0 <μ ≦ 0.5,
μ = mr / m,
ωr = sqrt (kb / mr),
k is an elastic coefficient of the spring when imitating vibration with relative deformation in a specific direction of the target structure in a one-mass system of spring and mass;
m is the mass of the mass point of the one mass system,
mr is the apparent inertial mass relative to the relative acceleration in a specific direction of the inertial connecting element;
kb is the elastic coefficient of the spring element,
sqrt (x) is the square root of x,
It was supposed to be.
With the configuration of the above embodiment,
The elastic coefficient kb of the spring element is a value between 90% and 110% of k × (2μ-1 + sqrt (1-2μ)) / (1-2μ);
The damping coefficient c of the damper element is a value between 90% and 110% of 2 × (4.436 μ ³ −3.619 μ ² +1.729 μ + 0.056) × ωr × mr.
As a result, the natural frequency ωr corresponding to the elastic coefficient kb of the spring element and the apparent inertial mass mr with respect to the relative acceleration in the specific direction of the inertial connection element and the natural vibration of the vibration mode displaced in the specific direction of the target structure. When the ratio between the excitation frequency ω and the natural frequency ωn is adjusted on the horizontal axis and the acceleration response magnification of the target structure is plotted on the vertical axis, the ratio to the number ωn is adjusted. Since the values at the two fixed points that are constant regardless of the value of the damping coefficient c of the damper element are substantially equal, the spring element at a frequency near the excitation frequency ω corresponding to the two fixed points. The acceleration response magnification determined by the elastic coefficient Kb of the inertial connection element and the inertial mass mr of the inertial connection element are substantially equal, and the damper element generates vibration energy along with a relative displacement along a specific direction of the inertial connection element. It is possible to reduce the level of the relative vibration response of the pair of portions that absorb and separate in the specific direction of the target structure.

  In order to achieve the above object, a vibration damping device for damping vibrations involving relative deformation in a specific direction of a target structure according to the present invention is provided with a linear motion shaft provided with a male screw and a female screw that fits the male screw. A viscous mass damper having a rotating body, a frame that rotatably supports the rotating body, an inner surface of the frame, and a viscous fluid sealed in a gap between the rotating body, an elastic body, and the elastic body sandwiched therebetween A spring element having a first member and a second member, and the target structure has a pair of attachment portions separated in a specific direction, and the linear motion direction and the specific direction of the linear motion shaft are substantially the same. Then, one of the frame or the linear motion shaft of the viscous mass damper is connected to one of the pair of mounting portions, and the other of the frame or the linear motion shaft of the viscous mass damper is connected to the first member of the spring element. A pair of the second members of the spring element Connected to the other attachment portions, and the things.

According to the configuration of the present invention, the viscous mass damper has a linear motion shaft provided with a male screw, a rotating body provided with a female screw fitted to the male screw, a frame that rotatably supports the rotating body, and an inner surface of the frame And a viscous fluid sealed in a gap between the rotating body. The spring element includes an elastic body and a first member and a second member sandwiching the elastic body. One of the frame or the linear motion shaft of the viscous mass damper is connected to one of the pair of mounting portions. The other of the viscous mass damper frame and the linear motion shaft is connected to the first member of the spring element. Connecting the second member of the spring element to the other of the pair of attachment parts;
As a result, when the target structure vibrates in a mode in which it moves relative to a specific direction, the vibration system composed of the viscous mass damper and the spring element oscillates, and the linear motion shaft is relatively displaced in the linear motion direction. Then, the rotating body rotates, a shearing force is generated in the viscous fluid, and the viscous fluid absorbs vibration energy.

  In order to achieve the above object, a vibration damping device for damping vibrations involving relative deformation in a specific direction of a target structure according to the present invention is provided with a linear motion shaft provided with a male screw and a female screw that fits the male screw. A viscous mass damper having a rotating body, a frame that rotatably supports the rotating body, an inner surface of the frame, and a viscous fluid sealed in a gap between the rotating body, and a plate member that extends in a direction crossing a specific direction. A spring element having a pair of attachment portions separated from each other by a target structure, the linear movement direction of the linear movement shaft substantially coincides with the specific direction, and one end of the plate member of the spring element is a pair of One of the viscous mass damper frame or linear motion shaft is fixed to one of the mounting portions, and one end of the plate member of the spring element is connected to the other end of the plate, and the other of the viscous mass damper frame or linear motion shaft is the target structure. Other than the pair of attachment parts of the object Linked, the other of the pair of the attachment portion is in a position spaced apart in a specific direction from the other end of the plate, and the things in.

According to the configuration of the present invention, the viscous mass damper includes a linear motion shaft provided with a male screw, a rotating body provided with a female screw fitted to the male screw, a frame that rotatably supports the rotating body, and an inner surface of the frame. And a viscous fluid enclosed in a gap between the rotating bodies. The spring element has a plate material extending in a direction crossing a specific direction. One end of the plate member of the spring element is fixed to one of the pair of attachment portions. One of the frame or the linear motion shaft of the viscous mass damper is connected to the other end of the plate member of the spring element. The other of the frame or the linear motion shaft of the viscous mass damper is connected to the other of the pair of attachment portions of the target structure.
As a result, when the target structure vibrates in a mode in which it moves relative to a specific direction, the vibration system composed of the viscous mass damper and the spring element oscillates, and the linear motion shaft is relatively displaced in the linear motion direction. Then, the rotating body rotates, a shearing force is generated in the viscous fluid, and the viscous fluid absorbs vibration energy.

  In order to achieve the above object, a vibration damping device for damping vibrations involving relative deformation in a specific direction of a target structure according to the present invention is provided with a linear motion shaft provided with a male screw and a female screw that fits the male screw. A viscous mass damper having a rotating body, a frame that rotatably supports the rotating body, a viscous fluid sealed between an inner surface of the frame and an outer surface of the rotating body, and an elastic body and the elastic body A spring element having a sandwiched first member and a second member, wherein the target structure has a pair of attachment portions spaced apart in a specific direction, and the linear motion direction and the specific direction of the linear motion shaft are approximately And the second member of the spring element is connected to one of the pair of mounting portions, the first member of the spring element is connected to the frame of the viscous mass damper, and the linear motion shaft of the viscous mass damper One end of the pair is connected to the other of the pair of mounting portions, and the front Across the one of the pair of the attachment portions of the objective structure to the other end of the linear axis of the viscous mass damper is connected to the other opposite side, and the things.

According to the configuration of the present invention, the viscous mass damper has a linear motion shaft provided with a male screw, a rotating body provided with a female screw fitted to the male screw, a frame that rotatably supports the rotating body, and an inner surface of the frame. And a viscous fluid enclosed between the outer surface of the rotating body. The spring element has an elastic body and a first member and a second member sandwiching the elastic body. The first member of the spring element is coupled to one of the pair of attachment portions. The second member of the spring element is coupled to the frame of the viscous mass damper. One end portion of the linear motion shaft of the viscous mass damper is connected to the other of the pair of attachment portions. The other end of the linear motion shaft of the viscous mass damper is connected to the opposite side of the other of the pair of attachment portions of the target structure.
As a result, when the target structure vibrates in a mode in which it moves relative to a specific direction, the vibration system composed of the viscous mass damper and the spring element oscillates, and the linear motion shaft is relatively displaced in the linear motion direction. Then, the rotating body rotates, a shearing force is generated in the viscous fluid, and the viscous fluid absorbs vibration energy.

  Hereinafter, a vibration damping device according to an embodiment of the present invention will be described. The present invention includes any of the embodiments described below, or a combination of two or more of them.

  The vibration damping device according to the embodiment of the present invention includes an elastic coefficient kb, which is a value obtained by dividing the reaction force generated when the spring element is displaced by a relative distance in a specific direction, and the viscous mass damper. Natural vibration corresponding to the apparent inertial mass mr, which is a value obtained by dividing the reaction force acting in the linear motion direction by the relative acceleration when the linear motion shaft is linearly moved in the linear motion direction at a predetermined relative acceleration. The ratio between the number ωr and the natural frequency ωn of the vibration mode displaced in a specific direction of the target structure is adjusted, the ratio between the excitation frequency ω and the natural frequency ωn is taken as the horizontal axis, and the response magnification of the target structure is When the vertical axis is taken, the reaction force acting in the linear motion direction when the linear motion shaft of the viscous mass damper is linearly moved at a constant relative speed on the line indicating the response magnification is the relative speed. Constant value regardless of the value of the damping coefficient c, which is the divided value The values at the two fixed points are substantially equal, and the response magnification is set so that one of the attachment portions of the target structure is subjected to an excitation force when the one attachment portion of the target structure is forcibly excited. Absolute response magnification, which is a ratio of amplitudes of one of the mounting parts of the target structure that vibrates in response to static displacement, of one of the mounting parts when the one mounting part of the target structure is forcibly excited The displacement response magnification, which is the ratio of the displacement and the displacement of the other mounting portion of the target structure that vibrates in response, or one of the target structures when the one mounting portion of the target structure is forcibly excited This is one of the acceleration response magnifications which is a ratio between the acceleration of the attachment portion and the acceleration of the other attachment portion of the target structure that vibrates in response.

The elastic coefficient kb, which is a value obtained by dividing the reaction force generated when the spring element is displaced by a relative distance in the linear motion direction, and the linear motion shaft of the viscous mass damper are predetermined in the linear motion direction. When the linear motion is caused by the relative acceleration, the natural frequency ωr corresponding to the apparent inertial mass mr, which is a value obtained by dividing the reaction force acting in the linear motion direction by the relative acceleration, and the displacement in the specific direction of the target structure. The ratio of the vibration mode to the natural frequency ωn is adjusted. When the horizontal axis represents the ratio of the excitation frequency ω and the natural frequency ωn, and the vertical axis represents one of the absolute response magnification, relative displacement response magnification, or acceleration response magnification of the target structure, the response The value of the damping coefficient c, which is a value obtained by dividing the reaction force acting in the linear motion direction by the relative velocity when the linear motion shaft of the viscous mass damper is linearly moved at a relative speed on a line indicating the magnification. Regardless of the time, the values at the two fixed points that are constant values are substantially equal.
As a result, at the frequency near the excitation frequency ω corresponding to two fixed points, the response magnification determined by the elastic coefficient Kb of the spring element and the inertia mass mr of the viscous mass damper becomes substantially equal, and the viscous mass The damper absorbs vibration energy with relative displacement between the frame and the linear motion shaft, and the level of relative vibration response of the pair of attachment portions that are separated in a specific direction of the target structure can be reduced.

Furthermore, in the vibration damping device according to the embodiment of the present invention, the damping coefficient c is adjusted so that the values at the two fixed points are substantially substantially maximized.
According to the configuration of the above embodiment, the attenuation coefficient c is adjusted, and the values at the two fixed points are substantially substantially maximized respectively.
As a result, the viscous mass damper has an appropriate damping coefficient c, absorbs vibration energy with the relative displacement of the frame and the direct coaxial, and corresponds to the absolute displacement of the target structure based on the support. Amplitude, relative displacement, or acceleration can be further reduced so that the relative vibration response level of the pair of mounting portions separated in a specific direction of the target structure does not exceed the response magnification corresponding to the two fixed points.

As described above, the seismic isolation device according to the present invention has the following effects due to its configuration.
The support and target are a viscous mass damper with a spring in which an inertia connecting element that converts relative displacement into a rotation amount and a damper element that generates a damping resistance force are connected in parallel and a spring element that generates an elastic reaction force is connected in series. Since the structure is coupled, when the target structure vibrates, the vibration system composed of the inertia connecting element and the spring element oscillates, and the inertia connecting element relatively displaces in parallel. The connected damper elements are relatively displaced to absorb vibration energy.
In addition, the specifications of the viscous mass damper with spring are set according to the vibration characteristics of the target structure, the response magnification of the target structure is optimized, and the frequency near the excitation frequency ω corresponding to the two fixed points is Since the response magnification determined by the elastic coefficient Kb of the spring element and the inertial mass mr of the inertial connection element is set to be substantially equal, the damper element is moved along with a relative displacement along a specific direction of the inertial connection element. By absorbing vibration energy, the level of vibration response of the target structure based on the support can be reduced.
In addition, the damping coefficient c is adjusted so that the values at the two fixed points are each substantially maximum, so that vibration energy is absorbed along with the relative displacement along the specific direction of the inertial connection element, A response magnification corresponding to two fixed points where the amplitude, relative displacement, or acceleration corresponding to the absolute displacement of the target structure based on the support is made smaller, and the level of vibration response of the target structure based on the support corresponds to two fixed points. Can not be exceeded.
In addition, the elastic coefficient kb of the spring element is obtained from the mass ratio μ and the elastic coefficient k of the main frame, and the damping coefficient c of the damper element is determined from the mass ratio μ, the apparent inertia mass mr of the inertia connecting element, and the inherent viscosity mass damper with the spring. Since the displacement response magnification of the target structure is optimized based on the frequency ωr, the elastic coefficient Kb of the spring element and the inertia are obtained at frequencies near the excitation frequency ω corresponding to two fixed points. The response magnification determined by the inertial mass mr of the connecting element is substantially equal, and the damper element absorbs vibration energy with relative displacement along a specific direction of the inertial connecting element, and the target structure based on the support The level of vibration response of an object can be reduced.
Further, the elastic coefficient kb of the spring element is obtained from the mass ratio μ and the elastic coefficient k of the main frame, and the damping coefficient c of the damper element is determined from the mass ratio μ, the apparent inertia mass mr of the inertia connecting element, and the viscous mass damper with spring. Since the acceleration response magnification of the target structure is optimized based on the natural frequency ωr of the target element, the elastic coefficient Kb of the spring element is obtained at a frequency in the vicinity of the excitation frequency ω corresponding to two fixed points. The response magnifications determined by the inertial mass mr of the inertial connection element are substantially equal, and the damper element absorbs vibration energy with relative displacement along a specific direction of the inertial connection element, and is based on a support. The level of vibration response of the target structure can be reduced.
In addition, a spring that directly connects a viscous mass damper in which a viscous fluid is sealed between the frame and the rotating body and a spring element made of an elastic body, which rotatably supports the rotating body fitted to the male screw of the linear motion shaft. Since the attached viscous mass damper connects the support and the target structure, when the target structure vibrates in a specific direction, the vibration system composed of the viscous mass damper and the spring element is coupled with vibration. Then, the linear motion shaft is relatively displaced in the linear motion direction, the rotating body rotates, a shearing force is generated in the viscous fluid, and the viscous fluid absorbs vibration energy.
In addition, the specifications of the viscous mass damper with spring are set according to the vibration characteristics of the target structure, the response magnification of the target structure is optimized, and the frequency near the excitation frequency ω corresponding to the two fixed points is The response magnification determined by the elastic coefficient Kb of the spring element and the inertial mass mr of the viscous mass damper becomes substantially equal, and the viscous mass damper absorbs vibration energy along with the relative displacement between the frame and the linear motion shaft. It can absorb and reduce the level of vibration response of the target structure based on the support.
In addition, since the damping coefficient c is adjusted so that the values at the two fixed points are substantially maximum, the vibration energy is absorbed along with the relative displacement of the frame and the direct coaxial, The amplitude, relative displacement, or acceleration corresponding to the absolute displacement of the underlying target structure is made smaller, and the vibration response level of the target structure based on the support does not exceed the response magnification corresponding to the two fixed points. You can

As described above, the vibration damping device according to the present invention has the following effects due to its configuration.
A viscous mass damper with a spring in which an inertial connection element that converts relative displacement into a rotation amount and a damper element that generates damping resistance and a spring element that generates elastic reaction force are connected in series Since a pair of locations separated in a specific direction are connected, when the target structure vibrates in a mode in which the target structure moves relative to the specific direction, a vibration system composed of the inertia connecting element and the spring element vibrates, Relative displacement of the inertial connecting element causes the damper elements connected in parallel to relatively displace to absorb vibration energy.
In addition, the specifications of the viscous mass damper with spring are set according to the vibration characteristics of the target structure, the response magnification of the target structure is optimized, and the frequency near the excitation frequency ω corresponding to the two fixed points is Since the response magnification determined by the elastic coefficient Kb of the spring element and the inertial mass mr of the inertial connection element is set to be substantially equal, the damper element is moved along with a relative displacement along a specific direction of the inertial connection element. The level of the relative vibration response of a pair of locations that absorb vibration energy and are separated in a specific direction of the target structure can be reduced.
In addition, since the damping coefficient c is adjusted so that the values at the two fixed points are substantially maximum respectively, the damper element has an appropriate damping coefficient c and is in a specific direction of the inertial connection element. The vibration energy is absorbed along with the relative displacement along, the amplitude, relative displacement, or acceleration of the target structure is made smaller, and the relative vibration response level of a pair of points separated in a specific direction of the target structure is reduced. It is possible to avoid exceeding the response magnification corresponding to the two fixed points.
In addition, the elastic coefficient kb of the spring element is obtained from the mass ratio μ and the elastic coefficient k of the main frame, and the damping coefficient c of the damper element is determined from the mass ratio μ, the apparent inertia mass mr of the inertia connecting element, and the inherent viscosity mass damper with the spring. Since the displacement response magnification of the target structure is optimized based on the frequency ωr, the elastic coefficient Kb of the spring element and the inertia are obtained at frequencies near the excitation frequency ω corresponding to two fixed points. The response magnifications determined by the inertial mass mr of the connection element are substantially equal, and the damper element absorbs vibration energy along with the relative displacement along the specific direction of the inertial connection element and is separated in the specific direction of the target structure. It is possible to reduce the relative vibration response level of the pair of locations.
In addition, the elastic coefficient kb of the spring element is obtained from the mass ratio μ and the elastic coefficient k of the main frame, and the damping coefficient c of the damper element is determined from the mass ratio μ, the apparent inertia mass mr of the inertia connecting element, and the inherent viscosity mass damper with the spring. Since the acceleration response magnification of the target structure is optimized from the frequency ωr, the elastic coefficient Kb of the spring element and the inertia are obtained at frequencies near the excitation frequency ω corresponding to two fixed points. The response magnifications determined by the inertial mass mr of the connection element are substantially equal, and the damper element absorbs vibration energy along with the relative displacement along the specific direction of the inertial connection element and is separated in the specific direction of the target structure. It is possible to reduce the relative vibration response level of the pair of locations.
In addition, a spring that directly connects a viscous mass damper in which a viscous fluid is sealed between the frame and the rotating body and a spring element made of an elastic body, which rotatably supports the rotating body fitted to the male screw of the linear motion shaft. Since the attached viscous mass damper is connected to a pair of mounting portions that are separated in a specific direction of the target structure, when the target structure vibrates in a mode in which the target structure moves relative to the specific direction, the viscous mass damper, the spring element, The vibration system constituted by the above is coupled with vibration, the linear motion shaft is relatively displaced in the linear motion direction, the rotating body rotates, shear force is generated in the viscous fluid, and the viscous fluid absorbs vibration energy. .
Also, with a spring that directly connects a viscous mass damper that encloses a viscous fluid between the frame and the rotating body, and a spring element made of a plate material, rotatably supporting the rotating body fitted to the male screw of the linear motion shaft Since the viscous mass damper is connected to a pair of mounting portions that are separated in a specific direction of the target structure, when the target structure vibrates in a mode in which the target structure moves relative to the specific direction, the viscous mass damper and the spring element The configured vibration system vibrates, the linear motion shaft relatively displaces in the linear motion direction, the rotating body rotates, shear force is generated in the viscous fluid, and the viscous fluid absorbs vibration energy.
In addition, a rotating mass fitted to the male screw of the linear motion shaft is rotatably supported, and a viscous mass damper in which a viscous fluid is sealed between the frame and the rotating body is connected to the target structure via a spring element. Since both ends of the linear motion shaft are connected to other mounting parts of the target structure, and the connected mounting parts are arranged in a specific direction, if the target structure vibrates in a mode in which it moves relative to the specific direction, The vibration system composed of the viscous mass damper and the spring element oscillates, the linear motion shaft is relatively displaced in the linear motion direction, the rotating body rotates, and shearing force is generated in the viscous fluid. The viscous fluid absorbs vibration energy.
In addition, the specifications of the viscous mass damper with spring are set according to the vibration characteristics of the target structure, the response magnification of the target structure is optimized, and the frequency near the excitation frequency ω corresponding to the two fixed points is The response magnification determined by the elastic coefficient Kb of the spring element and the inertial mass mr of the viscous mass damper becomes substantially equal, and the viscous mass damper absorbs vibration energy with relative displacement between the frame and the linear motion shaft. It is possible to reduce the relative vibration response level of the pair of attachment portions that absorb and separate in the specific direction of the elephant structure.
In addition, since the damping coefficient c is adjusted so that the values at the two fixed points are substantially maximum, the vibration energy is absorbed along with the relative displacement of the frame and the direct coaxial, The amplitude, relative displacement, or acceleration corresponding to the absolute displacement of the underlying target structure is made smaller, and the relative vibration response of a pair of mounting parts spaced apart in a specific direction of the support-based elephant structure is reduced. It is possible to prevent the level from exceeding the response magnification corresponding to the two fixed points.
Therefore, it is possible to provide a device capable of exhibiting a desired seismic isolation performance or vibration suppression performance with a simple structure, and a seismic isolation device and a vibration suppression device capable of easily setting the specifications of elements constituting the device.

The best mode for carrying out the present invention will be described below with reference to the drawings.
For convenience of explanation, the case where the acceleration of the earthquake shakes the building will be described as an example.

First, the seismic isolation device according to the first embodiment of the present invention will be described with reference to the drawings. FIG. 1 illustrates the seismic isolation device / vibration control device according to the first or fourth embodiment of the present invention. It is a conceptual diagram.

The seismic isolation device is a device for isolating the displacement in a specific direction of the target structure 10 supported by the main frame 20 on the basis of the support 5.
For example, the main frame 20 is a laminate of a plurality of resin plate materials.
The seismic isolation device includes an inertia connecting element 30, a spring element 40, and a damper element 50. A system in which the inertia connecting element 30 and the damper element 50 are connected in parallel and a system in which the spring element 40 is connected in series is a support. Connected to the target structure.
For convenience, a system in which the inertia connecting element 30 and the damper element 50 are connected in parallel is referred to as a viscous mass damper, and a system in which the viscous mass damper and the spring element 40 are connected in series is referred to as a spring-attached viscous mass damper.
For example, a viscous mass damper with a spring is placed between a support and a target structure, and both ends are connected in series to the support and the target structure.

The inertia connecting element 30 is an element that converts a relative displacement in a specific direction into a rotation amount of the rotating body.
For example, the inertia connecting element 30 converts the relative displacement in a specific direction into a rotation amount of the rotating body by a spiral structure. For example, when the rotating body has a predetermined rotational inertia ratio, the inertia connecting element generates an inertia force corresponding to the rotational inertia ratio in proportion to the relative acceleration in a specific direction.
The spring element 40 is an element that generates an elastic reaction force along a specific direction corresponding to a relative displacement in a specific direction. For example, when the spring element 40 has a predetermined elastic coefficient, the spring element 40 generates an elastic force corresponding to the elastic coefficient in proportion to the relative displacement.
The damper element 50 is an element that generates a damping resistance force corresponding to the relative speed in a specific direction. For example, when the damper element 50 has a predetermined damping coefficient c, the damper element 50 generates a damping force corresponding to the damping coefficient in proportion to the relative speed.

The method for determining the specifications of the seismic isolation device will be described below.
The natural frequency ωr corresponding to the elastic coefficient kb of the spring element and the apparent inertial mass mr with respect to the relative acceleration in the specific direction of the inertia connecting element, the vibration displaced in the specific direction of the system composed of the main frame and the target structure The ratio ωr / ωn with respect to the natural frequency ωn of the mode is adjusted, the ratio between the excitation frequency ω and the natural frequency ωn is taken as the horizontal axis, and the response magnification of the target structure is taken as the vertical axis, showing the response magnification. Regardless of the value of the damping coefficient c of the damper element on the line, the values at the two fixed points that are constant values are made substantially equal.
Here, the response magnification is the absolute response magnification, which is the ratio of the static displacement of the target structure due to the excitation force when the target structure is forced to vibrate and the amplitude of the target structure that vibrates in response. In response to the displacement response magnification, which is the ratio of the displacement of the support body when the body is forced to vibrate and the displacement of the target structure that vibrates in response, or the acceleration of the support body when the body is forced This is one of the acceleration response magnifications that is a ratio with the acceleration of the object to be vibrated.

The procedure for obtaining the specifications by the above method is as follows.
The structure composed of the seismic isolation device, the main frame, and the target structure is represented as a mass point model.
Create an equation of motion for the mass model.
When the response magnification is an absolute response magnification, an equation of motion for applying displacement forced vibration to the target structure of the mass model is created.
When the response magnification is the displacement response magnification, an equation of motion for applying displacement forced vibration to the end of the main frame of the mass model is created.
When the response magnification is the acceleration response magnification, an equation of motion is created that applies acceleration forced vibration to the end of the main frame of the mass model.
Solve the equation of motion and create an equation to find the response magnification.
Two intersection points P and Q of a response magnification curve with an attenuation coefficient c = 0 and a response magnification curve with an attenuation coefficient c = ∞ are obtained.
The curve is a response magnification drawn on a graph with the horizontal axis representing the ratio between the excitation frequency ω and the natural frequency ωn and the vertical axis representing the response magnification of the target structure.
A ratio value between the natural frequency ωr and the natural frequency ωn that makes the response magnification at the point P and the response magnification at the point Q equal is determined.
The specifications of the elements constituting the seismic isolation device are determined from the value of ωr / ωn.
ωr is a natural frequency corresponding to the elastic coefficient kb of the spring element and the apparent inertial mass mr with respect to the relative acceleration in a specific direction of the inertial connection element.
ωn is a natural frequency of a vibration mode that is displaced in a specific direction of a system composed of the main frame and the target structure.

When it is desired to reduce the displacement of the target structure, the response magnification is preferably the displacement response magnification.
When it is desired to reduce the acceleration of the target structure, the response magnification is preferably the acceleration response magnification.

Further, the attenuation coefficient c is adjusted so that the values at the two fixed points are substantially substantially maximized respectively. For example, the attenuation coefficient c is an average value of an attenuation coefficient cp that takes an extreme value at a point P and an attenuation coefficient cq that takes an extreme value at a point Q.
In this way, the response magnification does not exceed the value at the fixed point.

The procedure for obtaining the attenuation coefficient by the above method is as follows.
Create a formula for the response magnification into which the specifications obtained by the above procedure are substituted.
An attenuation coefficient cp with the point P as an extreme value of the response magnification is obtained.
An attenuation coefficient cq with the Q point as an extreme value of the response magnification is obtained.
The average value of the attenuation coefficient cp and the attenuation coefficient cq is adopted as the attenuation coefficient c that makes the values at the two fixed points approximately maximum.
The average value may be a value based on addition average, a value based on multiplication average, or a value based on other averages.

Hereinafter, description will be given of a method for determining specifications with an emphasis on reducing the displacement response magnification of the target structure with respect to the support.
The elastic coefficient kb of the spring element is a value between 90% and 110% of k × (1-2μ-sqrt (1-4μ)) / 2μ,
The damping coefficient c of the damper element is 2 × (31.095 μ ³ -12.04 μ ² +2.581 μ + 0.038) × ωr × mr between 90% and 110%, or the elastic coefficient kb of the spring element is k X (1-2μ + sqrt (1-4μ)) / 2μ between 70% and 160%,
The damping coefficient c of the damper element is one of values between 70% and 160% of 2 × (−18.558 μ ³ +4.880 μ ² −0.717 μ + 0.612) × ωr × mr.
here,
0 <μ ≦ 0.25,
μ = mr / m,
k is an elastic coefficient related to displacement along a specific direction of the main frame 20,
m is the mass of the target structure 10,
mr is the apparent inertial mass relative to the relative acceleration of the inertial connecting element 30 in a specific direction,
kb is the elastic coefficient of the spring element 40,
ωr = sqrt (kb / mr),
sqrt (x) is the square root of x.

A process of determining the elastic coefficient kb and the damping coefficient c will be described with reference to the drawings.
FIG. 15 is a graph 3 of the frequency ratio / damping constant-mass ratio according to the embodiment of the present invention.
Graph 3 shows the relationship between the frequency ratio βopt and the mass ratio μ optimized so as to reduce the displacement response magnification of the target structure, and the relationship between the optimized additional system 6 damping constant ζopt and the mass ratio μ. Indicates.
βopt = sqrt {(1-2μ-sqrt (1-4μ)) / 2μ ² },
βopt = sqrt {(1-2μ + sqrt (1-4μ)) / 2μ ² },
ζopt = 31.095μ ³ -12.04μ ² + 2.581μ + 0.038,
ζopt = −18.558 μ ³ +4.880 μ ² −0.717 μ + 0.612,
First, the mass ratio μ is determined. However, the mass ratio does not exceed 0.25.
The optimized frequency ratio βopt corresponding to the frequency ratio μ and the optimized damping constant ζopt are determined from the frequency ratio / damping constant-mass ratio graph shown in FIG.
The specifications are determined by the following equation: Kb = k × βopt ² × μ
c = 2 × ζopt × ωr × mr

When the seismic isolation device has the elastic coefficient kb of the spring element that satisfies the above formula, when the ratio of the excitation frequency ω and the natural frequency ωn is the horizontal axis and the displacement response magnification of the target structure is the vertical axis On the line indicating the displacement response magnification, the values at the two fixed points that are constant regardless of the value of the damping coefficient c of the damper element are substantially equal.
Further, if the seismic isolation device has the elastic coefficient kb and the damping coefficient c of the spring element that satisfies the above formula, the values at the two fixed points are substantially substantially maximized respectively.
Therefore, the displacement response magnification of the target structure can be reduced.

Below, the determination method of the specification which attaches importance to making the acceleration response with respect to the support body of a target structure small is demonstrated.
The elastic coefficient kb of the spring element is a value between 90% and 110% of k × (2μ-1 + sqrt (1-2μ)) / (1-2μ),
The damping coefficient c of the damper element is a value between 90% and 110% of 2 × (4.436 μ ³ −3.619 μ ² +1.729 μ + 0.056) × ωr / mr.
here,
0 <μ ≦ 0.5,
μ = mr / m,
k is an elastic coefficient related to displacement along a specific direction of the main frame 20,
m is the mass mr of the target structure 10, the apparent inertial mass kb relative to the relative acceleration in a specific direction of the inertial connection element 30 is the elastic coefficient of the spring element 40,
ωr = sqrt (kb / mr)
sqrt (x) is the square root of x.

The process of determining the elastic coefficient kb and the damping coefficient c will be described with reference to the drawings.
FIG. 16 is a graph 4 of the frequency ratio / damping constant-mass ratio according to the embodiment of the present invention.
Graph 4 shows the relationship between the frequency ratio βopt and the mass ratio μ optimized so as to reduce the acceleration response magnification of the target structure, and the relationship between the optimized damping constant ζopt and the mass ratio μ.
βopt = sqrt {(2μ-1 + sqrt (1-2μ)) / μ (1-2μ)},
ζopt = 4.436 μ ³ −3.619 μ ² +1.729 μ + 0.056,
First, the mass ratio μ is determined. However, the mass ratio does not exceed 0.5.
The optimized frequency ratio βopt and the optimized damping constant ζopt corresponding to the mass ratio μ are determined from the frequency ratio / damping constant-mass ratio graph shown in FIG.
According to the following formula: Kb = k × βopt ² × μ
c = 2 × ζopt × ωr × mr

When the seismic isolation device has the elastic coefficient kb of the spring element that satisfies the above formula, when the ratio of the excitation frequency ω and the natural frequency ωn is on the horizontal axis and the acceleration response magnification of the target structure is on the vertical axis On the line indicating the acceleration response magnification, the values at the two fixed points that are constant regardless of the value of the damping coefficient c of the damper element are substantially equal.
Further, if the seismic isolation device has the elastic coefficient kb and the damping coefficient c of the spring element that satisfies the above formula, the values at the two fixed points are substantially substantially maximized respectively.
Therefore, the acceleration response magnification of the target structure can be reduced.

Next, the seismic isolation device according to the second embodiment of the present invention will be described with reference to the drawings.
FIG. 2 is a conceptual diagram of the seismic isolation device according to the second embodiment of the present invention.
FIG. 12 is a conceptual diagram of the target structure of the present invention.
The seismic isolation device is a device for isolating a displacement in a specific direction of a target structure supported by a main frame on the basis of a support.
The seismic isolation device includes a viscous mass damper 100, a spring element 200, and a clevis 300, and a system in which the viscous mass damper 100, the spring element 200, and the clevis 300 are connected in series connects the support and the target structure.
FIG. 12 shows that the seismic isolation device is provided on the foundation of the building.

The viscous mass damper 100 will be described with reference to the drawings.
FIG. 10 is a cross-sectional view of a viscous mass damper according to an embodiment of the present invention.
FIG. 10 shows an example of the structure of the viscous mass damper.
The viscous mass damper 100 includes a linear motion shaft 120, a rotating body 130, a frame 140, and a viscous fluid 150.

The linear motion shaft 120 is a shaft body provided with a male screw.
At least one end of the linear motion shaft 120 is exposed to the outside of the frame 140 described later.

The rotating body 130 is a member provided with a female screw that fits into the male screw.
The rotating body 130 includes a screw nut 131 and a rotating cylinder 132.
The screw nut 131 is rotatably supported by a frame 140, which will be described later, and is provided with a female screw that fits into the male screw. The male screw and the female screw may be fitted together via bearing balls arranged in a row.
The rotating cylinder 132 is a hollow cylindrical member that is rotatably supported by a frame 140 described later.
The screw nut 131 and the rotating cylinder 132 are connected with their respective rotation centers coincident.
When the screw nut 131 rotates, the rotating cylinder 132 also rotates.
The frame 140 is a member that rotatably supports the rotating body, and includes a screw nut frame 141, a rotating cylindrical frame 142, and a bearing 143.
The screw nut frame 141 rotatably supports the screw nut 131 via the bearing 143. The rotating cylindrical frame 142 rotatably supports the rotating cylinder 132 via the bearing 143.
The viscous fluid 150 is a liquid sealed in a gap between the inner surface of the frame 140 and the rotating body.
For example, the viscous fluid 150 is sealed in a gap between the inner surface of the frame 140 and the outer periphery of the rotating body.

The viscous mass damper 100 corresponds to the “system in which inertia connection elements and damper elements are connected in parallel” described in the seismic isolation device according to the first embodiment of the present invention.
When the linear motion shaft 120 is relatively displaced in the linear motion direction in a state where the rotation of the frame 140 and the linear motion shaft 120 around the axis is constrained, the rotating body 130 corresponds to the inclination angle of the male screw and the female screw. Rotate by the rotation angle.
The apparent inertial mass mr with respect to the relative acceleration in a specific direction of the inertia connecting element is obtained by dividing the reaction force acting in the linear motion direction by the relative acceleration when the linear motion shaft is linearly moved in the linear motion direction at a predetermined relative acceleration. The value corresponds to the apparent inertial mass mr.
When the rotating body 130 rotates, the viscous fluid 150 enclosed in the gap between the rotating cylinder 132 and the rotating cylinder frame 142 causes a viscous force to act on the rotating cylinder 132.
The damping resistance force corresponding to the relative speed of the damper element in a specific direction matches the force acting in the linear motion direction of the linear motion shaft 120 by the viscous force.
The damping coefficient c, which is a value obtained by dividing the damping resistance force of the damper element by the relative speed, is the reaction force acting in the linear motion direction when the linear motion shaft 120 of the viscous mass damper is linearly moved at the relative speed. It corresponds to the attenuation coefficient c which is a divided value.

The spring element 200 is an element having a first member 220 and a second member 230 sandwiching the elastic body 210 and the elastic body.
FIG. 11 is a conceptual diagram of a spring element according to an embodiment of the present invention.
The elastic body 210 is an element that is elastically deformed.
For example, the elastic body 210 is a flexible material plate-shaped member that is elastically deformed by receiving a shearing force.
The first member 220 includes a flange 221 and a pair of elastic body support members 222 fixed to the flange.
The second member 230 includes a flange 231 and an elastic body support member 232 fixed to the flange.
The elastic body support member 222 and the elastic body support member 232 sandwich the elastic body 210.
When the first member 220 and the second member 230 move in directions away from each other, a shearing force is generated in the elastic body.
The spring element matches the direction in which the first member 220 and the second member 230 are separated from each other in a specific direction.

The spring element 200 corresponds to the spring element 40 described in the seismic isolation device according to the first embodiment of the present invention.
The elastic coefficient kb of the spring element 40 coincides with the elastic coefficient kb, which is a value obtained by dividing the reaction force generated when the spring element 200 is displaced by the relative distance in the linear motion direction by the relative distance.

The clevis 300 is a machine element that is interposed between two machine elements and is rotatable around an axis orthogonal to the direction connecting the two elements.
For example, the clevis 300 is interposed between the frame 140 of the viscous mass damper 100 and the support 5.
For example, the clevis 300 is interposed between the linear motion shaft 120 of the viscous mass damper 100 and the spring element 200.

Below, the attachment structure of the viscous mass damper with a spring is demonstrated.
The linear movement direction of the linear movement shaft 120 and the specific direction substantially coincide with each other, one of the frame 140 or the linear movement shaft 120 of the viscous mass damper 100 is connected to one of the support 5 and the target structure 10, and the viscous mass damper 100 is connected. The other of the frame 140 or the linear motion shaft 120 is connected to the first member 220 of the spring element, and the second member 230 of the spring element 200 is connected to the other of the support or the target structure.
In FIG. 2, the frame 140 of the viscous mass damper 100 is connected to the support 5 via the clevis 300, and the linear movement shaft 120 of the viscous mass damper 100 is connected to the first member 220 of the spring element 200 via the clevis 300. The second member 230 of the spring element 200 is fixed to one attachment portion 11 of the target structure 10.
The support 5 is a part of a foundation that rises from the foundation on which the target structure is installed.
One attachment portion of the target structure is a part of the target structure that projects downward from the bottom surface of the target structure.

Below, the setting method of the specification of the viscous mass damper with a spring is demonstrated.
The elastic coefficient kb, which is a value obtained by dividing the reaction force generated when the spring element 200 is displaced by the relative distance in the linear motion direction, and the linear motion shaft 120 of the viscous mass damper in the linear motion direction is a predetermined relative acceleration. The natural frequency ωr corresponding to the apparent inertial mass mr, which is the value obtained by dividing the reaction force acting in the linear motion direction by the relative acceleration, the main frame 20 and the target structure 10. The ratio of the natural frequency ωn of the vibration mode displaced in a specific direction of the system is adjusted, the ratio of the excitation frequency ω and the natural frequency ωn and ω / ωn is taken as the horizontal axis, and the response magnification of the target structure is A damping coefficient c that is a value obtained by dividing the reaction force acting in the linear motion direction by the relative velocity when the linear motion shaft of the viscous mass damper is linearly moved at the relative speed on the line indicating the response magnification. The values at the two fixed points that are constant regardless of the value of To.

  Here, the response magnification is the absolute response magnification, which is the ratio of the static displacement of the target structure due to the excitation force when the target structure is forced to vibrate and the amplitude of the target structure that vibrates in response. Response to the displacement response ratio, which is the ratio of the displacement of the support when the body is forced to vibrate and the displacement of the target structure that vibrates in response, or the acceleration of the support when the support is forced This is one of the acceleration response magnifications that is a ratio with the acceleration of the object that vibrates.

  The attenuation coefficient c is adjusted so that the values at the two fixed points are each substantially substantially maximal.

A method of adjusting the natural frequency ωr of the vibration system composed of the viscous mass damper and the spring element and the natural frequency ωn of the vibration system composed of the main frame 20 and the target structure 10 is shown in the figure. Based on this, a description will be given.
FIG. 13 is a graph 1 of the frequency ratio-displacement response magnification according to the first embodiment of the present invention.
In graph 1, the horizontal axis represents the frequency ratio ω / ωn, and the vertical axis represents the displacement response magnification, and the displacement in the specific direction of the support and the displacement in the specific direction of the mounting portion 11 of the target structure 10. The ratio is shown.
The solid line indicates the displacement response magnification when the spring-equipped viscous mass damper has the damping coefficient c set and optimized by the above method.
The broken line indicates the displacement response magnification when the spring-equipped viscous mass damper is set by the above method but the damping coefficient c is not zero but is an extremely small value.
The dashed line shows the case where the spring element is removed for comparison.
P point and Q point are two fixed points.
The natural frequency ωn of the vibration mode displaced in a specific direction of the system composed of the main frame 20 and the target structure 10 may be obtained by an excitation experiment or by an accelerometer provided in the target structure at the time of an earthquake. The acceleration data in a specific direction may be obtained by analysis, or may be obtained by calculation using a mathematical formula for obtaining the natural frequency from the elastic modulus k of the main frame and the mass of the target structure m.
In general, the specifications of the viscous mass damper and the spring element are such that the values of the two fixed points P and P at which the displacement response magnification curve of c = 0 and the displacement response magnification curve of c = ∞ intersect are equal. Is selected.
The attenuation coefficient c is selected so that the curve is substantially extreme at the two fixed points P1 and P2.
For example, the attenuation coefficient c is an average value of an attenuation coefficient cp that takes an extreme value at a point P and an attenuation coefficient cq that takes an extreme value at a point Q.

FIG. 14 is a graph 2 of the frequency ratio-acceleration response magnification according to the embodiment of the present invention.
In graph 2, the horizontal axis represents the frequency ratio ω / ωn, and the vertical axis represents the acceleration response magnification, and the acceleration in the specific direction of the support and the acceleration in the specific direction of the mounting portion 11 of the target structure 10 are shown. The ratio is shown.
The solid line represents the acceleration response magnification when the viscous mass damper with spring has the damping coefficient c set and optimized by the above method.
The broken line indicates the acceleration response magnification when the spring-equipped viscous mass damper is set by the above method but the damping coefficient c is not zero but is an extremely small value.
The dashed line shows the case where the spring element is removed for comparison.
P point and Q point are two fixed points.
The natural frequency ωn of the vibration mode displaced in a specific direction of the system composed of the main frame and the target structure may be obtained by an excitation experiment, or a specific direction by an accelerometer provided in the target structure at the time of an earthquake. May be obtained by analyzing the acceleration data, or may be obtained by calculation using an equation for obtaining the natural frequency from the elastic modulus k of the main frame and the mass of the target structure m.
In general, the specifications of the viscous mass damper and the spring element are selected so that the values of two fixed points P1 and P2 at which the acceleration response magnification curve of c = 0 and the acceleration response magnification curve of c = ∞ intersect are equal. To do.
The attenuation coefficient c is selected so that the curve is substantially extreme at the two fixed points P and Q. For example, the attenuation coefficient c is an average value of an attenuation coefficient cp that takes an extreme value at a point P and an attenuation coefficient cq that takes an extreme value at a point Q.

  As described in the seismic isolation device according to the first embodiment of the present invention, the specifications of the viscous mass damper with spring correspond to the mass ratio μ from the graph of frequency ratio / damping constant-mass ratio. The optimized frequency ratio βopt and the optimized damping constant ζopt may be determined, and the specifications may be obtained from the βopt and ζopt.

Next, a seismic isolation device according to a third embodiment of the present invention will be described with reference to the drawings.
FIG. 3 is a conceptual diagram of the seismic isolation device according to the third embodiment of the present invention.
The seismic isolation device is a device for isolating the displacement in a specific direction of the target structure 10 supported by the main frame 20 on the basis of the support.
The seismic isolation device includes a viscous mass damper 100, a spring element 200, and a clevis 300, and a system in which the viscous mass damper 100, the spring element 200, and the clevis 300 are connected in series connects the support and the target structure.

The viscous mass damper 100 includes a linear guide 110, a linear motion shaft 120, a rotating body 130, a frame 140, and a viscous fluid 150.
FIG. 10 shows the viscous mass damper 100 without the linear guide 110.
The linear guide 110 is an option, and is a mechanical element that restrains rotation of the linear motion shaft 120 around the axis.
For example, the linear guide 110 is fixed to the frame 140, meshes with a groove or a protrusion provided along the longitudinal direction on the side surface of the linear motion shaft 120, and restrains rotation around the axis of the linear motion shaft 120, Allow movement in the longitudinal direction.

  Since the structure of the linear motion shaft 120, the rotating body 130, the frame 140, and the viscous fluid 150 is the same as that of the seismic isolation device according to the second embodiment, the description thereof is omitted.

The spring element 200 is an element having a first member 220 and a second member 230 sandwiching the elastic body 210 and the elastic body.
The spring element 200 may be the one described in the seismic isolation device according to the second embodiment, or may be of another type.
In the following, other types will be described.
The elastic body 210 is an element that is elastically deformed.
For example, the elastic body 210 is a coil spring (not shown) extending in a specific direction.
The first member 220 includes a flange 221 and a pair of elastic body support members 222 fixed to the flange.
The second member 230 includes a flange 231 and an elastic body support member 232 fixed to the flange.
The elastic body support member 222 and the elastic body support member 232 sandwich the coil spring.
When the first member 220 and the second member 230 move in directions away from each other, the coil spring is bent.
The spring element matches the direction in which the first member 220 and the second member 230 are separated from each other in a specific direction.

  Since the clevis 300 is the same as that of the seismic isolation device according to the second embodiment of the present invention, description thereof is omitted.

  Since the method of using the seismic isolation device according to the third embodiment and the method of setting the specifications are the same as those of the seismic isolation device according to the second embodiment, description thereof is omitted.

Next, a vibration damping device according to a fourth embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a conceptual diagram of a seismic isolation device / damping device according to a first or fourth embodiment of the present invention.

The vibration damping device is a device that dampens vibration accompanied by relative deformation in a specific direction of the target structure.
For example, the vibration damping device is installed between a pair of mounting portions that are separated in a specific direction of the target structure, and is connected to the pair of mounting portions, and vibration energy of vibration accompanied by relative deformation in the specific direction of the target structure. Absorbs and suppresses vibration.
The vibration damping device includes an inertia connecting element 30, a spring element 40, and a damper element 50. A system in which the inertia connecting element 30 and the damper element 50 are connected in parallel and a system in which the spring element 40 is connected in series are coupled to a pair of attachment portions that are separated in a specific direction of the target structure.
For convenience, a system in which the inertia connecting element 30 and the damper element 50 are connected in parallel is referred to as a viscous mass damper, and a system in which the viscous mass damper and the spring element 40 are connected in series is referred to as a spring-attached viscous mass damper.
For example, a viscous mass damper with a spring is placed between a pair of attachment portions that are separated in a specific direction of the target structure, and both ends are connected in series to the pair of attachment portions.

  Since the structure of the viscous mass damper with a spring is the same as that of the seismic isolation device according to the first embodiment of the present invention, description thereof is omitted.

Hereinafter, a method for determining the specifications of the vibration control device will be described.
The ratio between the natural frequency ωr corresponding to the elastic coefficient kb of the spring element and the apparent inertial mass mr with respect to the relative acceleration in the specific direction of the inertia connecting element and the natural frequency ωn of the vibration mode displaced in the specific direction of the target structure , The ratio of the excitation frequency ω and the natural frequency ωn is the horizontal axis, and the response magnification of the target structure is the vertical axis, the value of the damping coefficient c of the damper element on the line indicating the response magnification Regardless of whether or not, the values at the two fixed points that are constant values are made substantially equal.
Here, the response magnification is the one location of the target structure that vibrates in response to the static displacement of one location of the target structure due to the excitation force when one location of the target structure is forcibly excited. The absolute response magnification, which is the ratio of the amplitude of the target structure, and the displacement, which is the ratio of the displacement of one location when one location of the target structure is forcibly vibrated and the displacement of the other location of the target structure that vibrates in response Acceleration response which is a ratio between the response rate or the acceleration of one part of the target structure when one part of the target structure is forcibly excited and the acceleration of the other part of the target structure that vibrates in response One of the magnifications.

The procedure for obtaining the specifications by the above method is as follows.
A location where the vibration control device for the target structure is attached is modeled into a one-mass system from a vibration mode that is displaced in a specific direction of the target structure and its natural frequency ωn.
The structure composed of the seismic isolation device and the target structure is expressed as a mass point model.
Create an equation of motion for the mass model.
When the response magnification is an absolute response magnification, an equation of motion for applying displacement forced vibration to the target structure of the mass model is created.
When the response magnification is the displacement response magnification, an equation of motion for applying displacement forced vibration to the end of the main frame of the mass model is created.
When the response magnification is the acceleration response magnification, an equation of motion is created that applies acceleration forced vibration to the end of the main frame of the mass model.
Solve the equation of motion and create an equation to find the response magnification.
Two intersection points P and Q of a response magnification curve with an attenuation coefficient c = 0 and a response magnification curve with an attenuation coefficient c = ∞ are obtained.
The curve is a response magnification drawn on a graph with the horizontal axis representing the ratio between the excitation frequency ω and the natural frequency ωn and the vertical axis representing the response magnification of the target structure.
The value of the ratio between the natural frequency ωr and the natural frequency ωn is determined so that the response magnification at the point P and the response magnification at the point Q are equal.
The specifications of the elements constituting the seismic isolation device are determined from the value of ωr / ωn.
ωr is a natural frequency corresponding to the elastic coefficient kb of the spring element and the apparent inertial mass mr with respect to the relative acceleration in a specific direction of the inertial connection element.
ωn is a natural frequency of a vibration mode that is displaced in a specific direction of the target structure.

When it is desired to reduce the displacement response of the target structure, the response magnification is preferably the displacement response magnification.
When it is desired to reduce the acceleration response of the target structure, the response magnification is said to be the acceleration response magnification.

  Further, the attenuation coefficient c is adjusted so that the values at the two fixed points are substantially substantially maximized respectively. For example, the attenuation coefficient c is an average value of an attenuation coefficient cp that takes an extreme value at a point P and an attenuation coefficient cq that takes an extreme value at a point Q.

The procedure for obtaining the attenuation coefficient by the above method is as follows.
Create a formula for the response magnification into which the specifications obtained by the above procedure are substituted.
An attenuation coefficient cp with the point P as an extreme value of the response magnification is obtained.
An attenuation coefficient cq with the Q point as an extreme value of the response magnification is obtained.
The average value of the attenuation coefficient cp and the attenuation coefficient cq is adopted as the attenuation coefficient c that makes the values at the two fixed points approximately maximum.
The average value may be a value based on addition average, a value based on multiplication average, or a value based on other averages.
In this way, the response magnification does not substantially exceed the values at the two fixed points.

A description will be given below of a method for determining specifications with an emphasis on reducing the displacement response in a specific direction at a pair of locations of the target structure.
The elastic coefficient kb of the spring element is a value between 90% and 110% of k × (1-2μ-sqrt (1-4μ)) / 2μ,
The damping coefficient c of the damper element is 2 × (31.095 μ ³ -12.04 μ ² +2.581 μ + 0.038) × ωr × mr between 90% and 110%, or the elastic coefficient kb of the spring element is k X (1-2μ + sqrt (1-4μ)) / 2μ between 70% and 160%,
The damping coefficient c of the damper element may be one of values between 70% and 160% of 2 × (−18.558 μ ³ +4.880 μ ² −0.717 μ + 0.612) × ωr × mr. .
here,
0 <μ ≦ 0.25,
μ = mr / m,
ωr = sqrt (kb / mr)
k is an elastic coefficient of the spring when imitating vibration with relative deformation in a specific direction of the target structure in a one-mass system of spring and mass;
m is the mass of the mass point of the one mass system,
mr is the apparent inertial mass kb relative to the relative acceleration in a specific direction of the inertia connecting element 30 is the elastic coefficient of the spring element 40;
sqrt (x) is the square root of x.
In this way, the displacement response magnification of the target structure can be reduced.

Since the process of determining the elastic coefficient kb and the damping coefficient c is the same as that of the seismic isolation device according to the first embodiment of the present invention, the description thereof is omitted.
The elastic coefficient k and mass m of the target structure are the elastic coefficient of the spring and the mass of the mass when imitating the vibration in a specific direction of a pair of locations of the target structure in a one-mass system composed of the mass and the spring. is there.
Here, the mass m of the target structure may be obtained by calculation using the design data of the target structure.

When the seismic isolation device has the elastic coefficient kb of the spring element that satisfies the above equation, the ratio of the excitation frequency ω and the natural frequency ωn is taken as the horizontal axis, and a pair of locations separated in a specific direction of the target structure When the displacement response magnification is taken as the vertical axis, the values at two fixed points that are constant values are substantially equal on the line indicating the displacement response magnification regardless of the value of the damping coefficient c of the damper element.
Further, if the seismic isolation device has the elastic coefficient kb and the damping coefficient c of the spring element that satisfies the above formula, the values at the two fixed points are substantially substantially maximized respectively.
Therefore, the displacement response magnification of the target structure can be reduced.

Below, the determination method of the specification which attaches importance to making the acceleration response with respect to the support body of a target structure small is demonstrated.
The elastic coefficient kb of the spring element is a value between 90% and 110% of k × (2μ-1 + sqrt (1-2μ)) / (1-2μ),
The damping coefficient c of the damper element may be a value between 90% and 110% of 2 × (4.436 μ ³ −3.619 μ ² +1.729 μ + 0.056) × ωr × mr.
here,
0 <μ ≦ 0.5,
μ = mr / m,
ωr = sqrt (kb / mr),
k is an elastic coefficient of the spring when imitating vibration with relative deformation in a specific direction of the target structure in a one-mass system of spring and mass;
m is the mass of the mass point of the one mass system,
mr is the apparent inertial mass kb relative to the relative acceleration in a specific direction of the inertia connecting element 30 is the elastic coefficient of the spring element 40;
sqrt (x) is the square root of x.
In this way, the acceleration response magnification of the target structure can be reduced.

  Since the process of determining the elastic coefficient kb and the damping coefficient c is the same as that of the seismic isolation device according to the first embodiment of the present invention, the description thereof is omitted.

When the seismic isolation device has the elastic coefficient kb of the spring element that satisfies the above formula, when the ratio of the excitation frequency ω and the natural frequency ωn is on the horizontal axis and the acceleration response magnification of the target structure is on the vertical axis On the line indicating the acceleration response magnification, the values at the two fixed points that are constant regardless of the value of the damping coefficient c of the damper element are substantially equal.
Further, if the seismic isolation device has the elastic coefficient kb and the damping coefficient c of the spring element that satisfies the above formula, the values at the two fixed points are substantially substantially maximized respectively.
Therefore, the acceleration response magnification of the target structure can be reduced.

Next, a vibration control device according to a fifth embodiment of the present invention will be described with reference to the drawings.
FIG. 4 is a conceptual diagram of a vibration damping device according to the fifth embodiment of the present invention.
FIG. 12 is a conceptual diagram of the target structure of the present invention.
The vibration damping device is a device that dampens vibration accompanied by relative deformation in a specific direction of the target structure.
The vibration damping device includes a viscous mass damper 100, a spring element 200, and a clevis 300, and a system in which the viscous mass damper 100, the spring element 200, and the clevis 300 are connected in series connects a pair of attachment portions of the target structure. .
FIG. 12 shows that the vibration damping device is provided on the third floor of the building.

  Since the structures of the viscous mass damper 100, the spring element 200, and the clevis 300 are the same as those used in the seismic isolation device according to the second embodiment of the present invention, description thereof is omitted.

Below, the attachment structure of the viscous mass damper with a spring is demonstrated.
The target structure has a pair of attachment parts 12, 13 spaced apart in a specific direction,
The linear motion direction of the linear motion shaft and the specific direction are approximately the same,
Connect one of the viscous mass damper frame or linear motion shaft to one of the pair of mounting parts,
Connect the other of the viscous mass damper frame or the linear motion shaft to the first member of the spring element,
The second member of the spring element is connected to the other of the pair of attachment portions.
In FIG. 4, the frame 140 of the viscous mass damper 100 is connected to one mounting portion 12 of the pair of mounting portions of the target structure via the clevis 300, and the linear movement shaft 120 of the viscous mass damper 100 is connected to the first of the spring elements 200. The second member 230 of the spring element is connected to the one member 220 and is fixed to the other attachment portion 13 of the target structure 10.
One mounting portion 12 of the target structure is a mounting seat fixed to a beam member of the target structure.
The other attachment portion 13 of the target structure is an intersection of the lower ends of a pair of diagonal members protruding obliquely from two locations of the beam material of the target object.
The direction of attaching the viscous mass damper with the spring may be opposite.

Below, the setting method of the specification of a viscous mass damper with a spring is demonstrated.
Linearly move the elastic force kb, which is the reaction force generated when the spring element is displaced by a relative distance in a specific direction, divided by the relative distance, and the linear motion axis of the viscous mass damper in the linear motion direction at a predetermined relative acceleration. The natural frequency ωr corresponding to the apparent inertial mass mr, which is a value obtained by dividing the reaction force acting in the linear motion direction by the relative acceleration, and the natural frequency of the vibration mode displaced in a specific direction of the target structure. The ratio of ωn is adjusted, the ratio of excitation frequency ω and natural frequency ωn is the horizontal axis, and the response magnification of the target structure is the vertical axis. Values at two fixed points that are constant regardless of the value of the damping coefficient c, which is the value obtained by dividing the reaction force acting in the linear motion direction by the relative velocity when the linear motion shaft is linearly moved at the relative velocity. May be substantially equal.

  Here, the response magnification is the one of the target structure that vibrates in response to the static displacement of one mounting portion of the target structure due to the excitation force when one part of the target structure is forcibly excited. Absolute response magnification, which is the ratio of the amplitudes of the parts, and the ratio of the displacement of one part when one part of the target structure is forcibly excited to the displacement of the other part of the target structure that has vibrated in response Acceleration response, which is the ratio between the displacement response magnification or the acceleration of one part of the target structure when one part of the target structure is forcibly excited and the acceleration of the other part of the target structure that has vibrated in response One of the magnifications,

    The attenuation coefficient c is adjusted so that the values at the two fixed points are each substantially substantially maximal.

A method of adjusting the natural frequency ωr of the vibration system composed of the viscous mass damper and the spring element and the natural frequency ωn of the vibration mode displaced in a specific direction of the target structure will be described with reference to the drawings. To do.
FIG. 13 is a graph 1 of the frequency ratio-displacement response magnification according to the embodiment of the present invention.
FIG. 13 shows the displacement in a specific direction of one attachment portion 12 of a pair of attachment portions of the target structure and the target structure when the frequency ratio ω / ωn is taken on the horizontal axis and the displacement response magnification is taken on the vertical axis. The ratio of the displacement of the other attachment part 13 of the thing 10 in the specific direction is shown.
The solid line indicates the displacement response magnification when the spring-equipped viscous mass damper has the damping coefficient c set and optimized by the above method.
The broken line indicates the displacement response magnification when the spring-equipped viscous mass damper is set by the above method, but the damping coefficient c is a small value close to zero.
The dashed line shows the case where the spring element is removed for comparison.
P point and Q point are two fixed points.
The natural frequency ωn of the vibration mode that is displaced in a specific direction of the target structure may be obtained by an excitation experiment, or acceleration data in a specific direction of a pair of attachment portions by an accelerometer provided in the target structure at the time of an earthquake. It may be obtained by analysis, or the natural frequency may be obtained from design data of the target structure.
In general, the specifications of the viscous mass damper and the spring element are such that the values of the two fixed points P and P at which the displacement response magnification curve of c = 0 and the displacement response magnification curve of c = ∞ intersect are equal. Is selected.
Thereafter, the attenuation coefficient c is selected so that the curve substantially takes extreme values at the two fixed points P1 and P2.

FIG. 14 is a graph 1 of the frequency ratio-acceleration response magnification according to the embodiment of the present invention.
In FIG. 14, the horizontal axis represents the frequency ratio ω / ωn, and the vertical axis represents the acceleration response magnification, and the acceleration of one mounting portion 12 of the pair of mounting portions of the target structure and the target structure 10 The ratio of the acceleration of the specific direction of the other attaching part 13 is shown.
The solid line indicates the displacement response magnification when the spring-equipped viscous mass damper has the damping coefficient c set and optimized by the above method.
The broken line indicates the displacement response magnification when the spring-equipped viscous mass damper is set by the above method, but the damping coefficient c is a small value close to zero.
The dashed line shows the case where the spring element is removed for comparison.
P point and Q point are two fixed points.
The natural frequency ωn of the vibration mode displaced in a specific direction of the system composed of the main frame and the target structure may be obtained by an excitation experiment, or a specific direction by an accelerometer provided in the target structure at the time of an earthquake. May be obtained by analyzing the acceleration data, or may be obtained by calculation using an equation for obtaining the natural frequency from the elastic modulus k of the main frame and the mass of the target structure m.
In general, the specifications of the viscous mass damper and spring element are selected so that the values of the two fixed points P1 and P2 at which the displacement response magnification curve of c = 0 and the displacement response magnification curve of c = ∞ intersect are equal. To do.
The attenuation coefficient c is selected so that the curve is substantially extreme at the two fixed points P1 and P2. For example, the attenuation coefficient c is an average value of an attenuation coefficient cp that takes an extreme value at a point P and an attenuation coefficient cq that takes an extreme value at a point Q.

  As described in the vibration damping device according to the embodiment of the present invention, the specifications of the viscous mass damper with spring are optimized corresponding to the mass ratio μ from the graph of the frequency ratio / damping constant-mass ratio. Alternatively, the frequency ratio βopt and the optimized damping constant ζopt may be determined, and the specifications may be obtained from the βopt and ζopt.

Next, a vibration control device according to a sixth embodiment of the present invention will be described with reference to the drawings.
FIG. 5 is a conceptual diagram of a vibration damping device according to the sixth embodiment of the present invention.

The vibration damping device is a device for damping relative deformation in a specific direction of the target structure.
The vibration damping device includes a viscous mass damper 100, a spring element 400, and a clevis 300, and connects a system in which the viscous mass damper 100, the spring element 400, and the clevis 300 are connected in series to a pair of attachment portions of the target structure. .
FIG. 12 shows that the vibration damping device is provided on the fourth floor of the building.

  Since the structure of the viscous mass damper 100 is the same as that of the seismic isolation device according to the fifth embodiment of the present invention, the description thereof is omitted.

The spring element 400 includes a plate member 410 extending in a direction crossing a specific direction and a mounting flange 420 fixed to one end of the plate member.
The plate material 410 bends within the elastic limit in the plate thickness direction.
For example, the plate material 410 is a plate material made of spring steel.
For example, the plate material 410 is a plate material in which a plurality of plate materials are stacked in the plate thickness direction.
For example, the plate material 410 is a composite material in which a metal plate and a resin plate are laminated in the plate thickness direction.

Below, the attachment structure of the viscous mass damper with a spring is demonstrated.
The target structure 10 has a pair of mounting portions spaced apart from each other, the linear motion direction of the linear motion shaft 120 and the specific direction substantially coincide with each other, and one end 411 of the plate 410 of the spring element 400 is one mounting of the pair of mounting portions. One of the frame 140 and the linear motion shaft 120 of the viscous mass damper 100 is connected to the other end 412 of the plate of the spring element 400, and the other of the frame 140 and the linear motion shaft 120 of the viscous mass damper 100 is the target structure. It connects with the other attachment part of a pair of attachment part of the thing 10, and the other of a pair of attachment part exists in the position spaced apart in the specific direction from the other end 412 of a board | plate material.
FIG. 5 shows that the mounting flange 420 of the spring element 400 is fixed to the beam material above the target structure, and the lower end of the plate material 410 hangs downward.
The frame 140 of the viscous mass damper 100 is connected to the beam member mounting portion 12 below the target structure via the clevis 300, and the linear movement shaft 120 of the viscous mass damper 100 is connected to the plate member 410 of the spring element 400 via the clevis 300. Connected to the lower end 412.

  Since the specification method of the specification of the spring-loaded viscous mass damper is the same as that of the vibration damping device according to the fifth embodiment, the description thereof is omitted.

Next, a vibration control device according to a seventh embodiment of the present invention will be described with reference to the drawings.
FIG. 6 is a conceptual diagram of a vibration damping device according to the seventh embodiment of the present invention.
FIG. 12 is a conceptual diagram of the target structure of the present invention.
The vibration damping device includes a viscous mass damper 100, a spring element 400, and a pair of clevises 300, and a system in which the viscous mass damper 100, the spring element 400, and the clevis 300 are connected in series is a pair of attachment portions of the target structure. Connected.
FIG. 12 shows that the vibration damping device is provided on the fourth floor of the building.

  Since the structure of the viscous mass damper 100, the spring element 400, and the clevis 300 is the same as that used in the first seismic isolation device of the present invention, the description thereof is omitted.

Below, the attachment structure of the viscous mass damper with a spring is demonstrated.
The target structure 10 has a pair of mounting portions spaced apart from each other, the linear motion direction of the linear motion shaft 120 and the specific direction substantially coincide, and one of the frame 140 of the viscous mass damper 100 or the linear motion shaft 120 is attached to a pair. The other of the viscous mass damper 100 is connected to the first member 220 of the spring element 200, and the second member 230 of the spring element 200 is connected to a pair of attachments. It connects with the other attachment part 13 of a part.
FIG. 6 shows a spring element via two clevises 300 in which the frame 140 of the viscous mass damper 100 is fixed to one of a pair of attachment portions 12 of the target structure and the linear motion shaft 120 of the viscous mass damper 100 is connected in series. It is shown being connected to the other end 412 of 400.

  Since the specification method of the specification of the spring-loaded viscous mass damper is the same as that of the vibration damping device according to the fifth embodiment, the description thereof is omitted.

Next, a vibration control device according to an eighth embodiment of the present invention will be described with reference to the drawings.
FIG. 7 is a conceptual diagram of a vibration damping device according to the eighth embodiment of the present invention.
FIG. 12 is a conceptual diagram of the target structure of the present invention.
The vibration damping device includes a viscous mass damper 100, a spring element 200, and a pair of clevises 300. A system in which the viscous mass damper 100, the spring element 200, and the clevis 300 are connected in series is a pair of attachment portions of the target structure. Connected.
FIG. 12 shows that the vibration damping device is provided on the second floor of the building.

  Since the structures of the viscous mass damper 100, the spring element 200, and the clevis 300 are the same as those used in the first seismic isolation device of the present invention, description thereof is omitted.

Below, the attachment structure of the viscous mass damper with a spring is demonstrated.
The target structure 10 has a pair of mounting portions 12 and 13 that are spaced apart in a specific direction. The linear movement direction of the linear motion shaft 120 and the specific direction substantially coincide with each other, and the frame 140 or the linear motion shaft 120 of the viscous mass damper 100 is obtained. Is connected to one mounting portion 12 of the pair of mounting portions, the other of the frame 140 of the viscous mass damper 100 or the linear motion shaft 120 is connected to the first member 220 of the spring element 200, and the second of the spring element 200 is connected. The member 230 is connected to the other attachment portion 13 of the pair of attachment portions.
The specific direction is directed to the oblique direction of the target structure.
One attachment portion 12 of the target structure is located on the upper portion of the lower beam, and the other attachment portion 13 is located on the lower surface of the upper beam.
In FIG. 7, the frame 140 of the viscous mass damper 100 in which the linear motion direction is inclined is fixed to one mounting portion 12 of the pair of mounting portions of the target structure via the clevis 300, and the linear motion of the viscous mass damper 100 is performed. The shaft 120 is shown connected to the first member of the target structure 10 via the spring element 200.

  Since the specification method of the specification of the spring-loaded viscous mass damper is the same as that of the vibration damping device according to the fifth embodiment, the description thereof is omitted.

Next, a vibration damping device according to a ninth embodiment of the present invention will be described with reference to the drawings.
FIG. 8 is a conceptual diagram of a vibration damping device according to the ninth embodiment of the present invention.
FIG. 12 is a conceptual diagram of the target structure of the present invention.
The vibration damping device includes a viscous mass damper 100, a spring element 200, and a pair of clevises 300, and a system in which the viscous mass damper 100, the spring element 200, and the clevis 300 are connected in series connects a pair of locations of the target structure. To do.
FIG. 12 shows that the vibration damping device is provided on the first floor of the building.

  Since the structures of the viscous mass damper 100, the spring element 200, and the clevis 300 are the same as those used in the first seismic isolation device of the present invention, description thereof is omitted.

Below, the attachment structure of the viscous mass damper with a spring is demonstrated.
The target structure has a pair of attachment parts spaced apart in a specific direction,
The linear movement direction of the linear motion shaft 120 and the specific direction substantially coincide with each other, and one of the frame 140 of the viscous mass damper 100 or the linear motion shaft 120 is connected to one mounting portion 12 of the pair of mounting portions. The other of the frame 140 or the linear motion shaft 120 is connected to the first member 220 of the spring element 200, and the second member of the spring element 200 is connected to the other attachment portion 13 of the pair of attachment portions 230.
The specific direction is directed in the vertical direction of the target structure.
One attachment portion 12 of the target structure is located on the upper portion of the lower beam, and the other attachment portion 13 is located on the lower surface of the upper beam.
FIG. 8 shows that the frame 140 of the viscous mass damper 100 whose linear motion direction is in the vertical direction is fixed to one mounting portion 12 of the pair of mounting portions of the target structure via the clevis 300, and It shows that the moving shaft 120 is connected to the first member of the target structure 10 via a spring element.

  Since the specification method of the specification of the spring-loaded viscous mass damper is the same as that of the vibration damping device according to the fifth embodiment, the description thereof is omitted.

Next, a vibration damping device according to a tenth embodiment of the present invention will be described with reference to the drawings.
FIG. 9 is a conceptual diagram of a vibration damping device according to the ninth embodiment of the present invention.
FIG. 12 is a conceptual diagram of the target structure of the present invention.
The vibration damping device includes a viscous mass damper 100 and a spring element 200, and a system in which the viscous mass damper 100, the spring element 200, and the clevis 300 are connected in series is coupled to a pair of attachment portions of the target structure.
FIG. 12 shows that the vibration damping device is provided on the first floor of the building.

The structures of the viscous mass damper 100, the spring element 200, and the clevis 300 are almost the same as those used in the first seismic isolation device of the present invention.
The difference is that both ends of the linear motion shaft are exposed from each frame.

Below, the attachment structure of the viscous mass damper with a spring is demonstrated.
The target structure 10 has a pair of attachment portions that are spaced apart in a specific direction, and the linear movement direction of the linear movement shaft 120 and the specific direction substantially coincide with each other, and the first member 220 of the spring element 200 is connected to one of the pair of attachment portions. And the second member 230 of the spring element 200 is connected to the frame of the viscous mass damper 100, and one end of the linear motion shaft 120 of the viscous mass damper 100 is connected to the other of the pair of attachment parts. The other end portion of the linear motion shaft 120 of the damper 100 is connected to the mounting portion 14 on the opposite side across the one mounting portion 13 of the pair of mounting portions of the target structure 10.
FIG. 9 shows that the first member 220 of the spring element 200 is fixed to the frame 140 of the viscous mass damper 100 whose linear movement direction is in the horizontal direction, and the second member 230 of the spring element 200 is a pair of attachment portions of the target structure. It shows that the both ends of the linear motion shaft are fixed to the target structure respectively.

  Since the specification method of the specification of the spring-loaded viscous mass damper is the same as that of the vibration damping device according to the fifth embodiment, the description thereof is omitted.

Numerical analysis results obtained by optimizing and evaluating the specifications of the seismic isolation device / damping device according to the first or fourth embodiment for each of the three types of response magnification will be described.
FIG. 17 is a graph showing the numerical analysis results of Example 1 of the present invention.
The upper graph in FIG. 17 shows the displacement response magnification.
The lower graph of FIG. 17 shows the acceleration response magnification.
In the legend of FIG. 17, when the specifications are determined with an emphasis on reducing the absolute response magnification at the time of the dynamic optimum design, the specifications with an emphasis on reducing the displacement response magnification at the time of the optimum displacement design. Is determined when specifications are determined with an emphasis on reducing the acceleration response magnification at the time of optimum acceleration design.
The case where the mass ratio μ was 0.1 and 0.2 was evaluated.
From FIG. 17, the peak of the dynamic optimal design system has the largest peak for both displacement and acceleration. Comparing the optimal displacement design with the optimal acceleration design, the peak value of the resonance curve is low. However, the peak value is smaller in the optimal displacement design at the higher resonance point. Which is more appropriate as the optimum design depends on the characteristics of the system disturbance. It has been found.

The damping performance of the damping device according to the seventh embodiment was confirmed by a model test.
FIG. 18 is an external view of a model test apparatus according to Embodiment 2 of the present invention.
FIG. 19 is a result table of a model test of Example 2 of the present invention.
In the model test apparatus, the steel plate supported by the LM guide simulates the target structure, and the coil spring simulates elasticity between a pair of locations of the main frame or the target structure. The upper end of the plate material of the spring element is fixed to the lower surface of the steel plate. The end of the inertia connecting element is connected to the lower end of the plate of the spring element.
The base is vibrated and the acceleration of the steel plate is measured with an accelerometer placed on top of the steel plate. Integrate acceleration and convert to displacement.
FIG. 19 shows the maximum response value and response reduction rate of the optimum design system in the design artificial seismic wave (BCL-L2) and the four actual seismic waves.
From the table of FIG. 19, it is clear that the vibration of the target structure can be well isolated or controlled when the displacement response magnification is optimized or the acceleration response magnification is optimized.

As described above, the seismic isolation device according to the present invention has the following effects due to its configuration.
A viscous mass damper with a spring in which a system in which an inertial connection element 30 that converts relative displacement into a rotation amount and a damper element 50 that generates a damping resistance force are connected in parallel and a spring element 40 that generates an elastic reaction force is connected in series is supported. Since the body 5 and the target structure 10 are connected to each other, when the target structure 10 supported by the main frame vibrates, a vibration system including the inertia connecting element 30 and the spring element 40 is coupled to vibration. Then, the inertia connecting element 30 is relatively displaced, and the damper elements 50 connected in parallel are relatively displaced to absorb vibration energy.
In addition, the specifications of the viscous mass damper with spring are set according to the vibration characteristics of the target structure, the response magnification of the target structure is optimized, and the frequency near the excitation frequency ω corresponding to the two fixed points is Since the response magnification determined by the elastic coefficient Kb of the spring element 40 and the inertial mass mr of the inertial connection element 30 is made substantially equal, the damper element 50 vibrates with relative displacement along the specific direction of the inertial connection element 30. The level of vibration response of the target structure 10 based on the support 5 can be reduced by absorbing energy.
In addition, since the damping coefficient c is adjusted so that the values at the two fixed points P and Q are substantially maximized, the vibration energy is absorbed along with the relative displacement along the specific direction of the inertial connection element 30. The amplitude, relative displacement, or acceleration corresponding to the absolute displacement of the target structure 10 based on the support 5 is made smaller, and the level of vibration response of the target structure 10 based on the support 5 is two fixed points. It is possible to avoid exceeding the response magnification corresponding to p and Q.
In addition, the elastic coefficient kb of the spring element is obtained from the mass ratio μ and the elastic coefficient k of the main frame, and the damping coefficient c of the damper element is determined from the mass ratio μ, the apparent inertia mass mr of the inertia connecting element, and the inherent viscosity mass damper with the spring. Since the displacement response magnification of the target structure is optimized based on the frequency ωr, the elastic coefficient Kb of the spring element and the inertia connecting element are used at frequencies near the excitation frequency ω corresponding to the two fixed points. The response magnification determined by the inertia mass mr is substantially equal, the damper element absorbs vibration energy with relative displacement along the specific direction of the inertia connection element, and the vibration response of the target structure based on the support The level can be reduced.
Further, the elastic coefficient kb of the spring element is obtained from the mass ratio μ and the elastic coefficient k of the main frame, and the damping coefficient c of the damper element is determined from the mass ratio μ, the apparent inertia mass mr of the inertia connecting element, and the viscous mass damper with spring. Since the acceleration response magnification of the target structure is optimized from the natural frequency ωr of the object, the elastic coefficient Kb and inertia of the spring element are obtained at frequencies near the excitation frequency ω corresponding to the two fixed points. The response magnification determined by the inertial mass mr of the connecting element becomes substantially equal, and the damper element absorbs vibration energy along with the relative displacement along the specific direction of the inertial connecting element, and the vibration of the target structure based on the support body. The level of response can be reduced.
In addition, a spring element 200 made of an elastic body and a viscous mass damper in which a viscous fluid 150 is sealed between the frame 130 and the rotating body 130 by rotatably supporting the rotating body 130 fitted to the male screw of the linear motion shaft 120. Since the viscous mass damper with a spring directly connecting the support body 5 and the target structure 10 is coupled, when the target structure 10 vibrates in a specific direction, the viscous mass damper 100 and the spring element 200 The configured vibration system vibrates, the linear motion shaft 120 is relatively displaced in the linear motion direction, the rotating body 130 rotates, a shearing force is generated in the viscous fluid 150, and the viscous fluid 150 absorbs vibration energy. .
In addition, the specifications of the viscous mass damper with spring are set in accordance with the vibration characteristics of the target structure 10, the response magnification of the target structure 10 is optimized, and the frequencies near the excitation frequency ω corresponding to the two fixed points. , The response magnification determined by the elastic coefficient Kb of the spring element and the inertial mass mr of the viscous mass damper is substantially equal, and the viscous mass damper absorbs vibration energy in association with the relative displacement between the frame and the linear motion shaft. The level of the vibration response of the target structure based on can be reduced.
In addition, the damping coefficient c is adjusted so that the values at the two fixed points are substantially maximum, so that the vibration energy is absorbed along with the relative displacement of the frame and the direct coaxial, and the object is based on the support. The amplitude, relative displacement, or acceleration corresponding to the absolute displacement of the structure can be further reduced so that the vibration response level of the target structure based on the support does not exceed the response magnification corresponding to the two fixed points.

As described above, the vibration damping device according to the present invention has the following effects due to its configuration.
A viscous mass damper with a spring in which a system in which an inertia connecting element 30 that converts relative displacement into a rotation amount and a damper element 50 that generates a damping resistance force are connected in parallel and a spring element 40 that generates an elastic reaction force is connected in series is an object. Since a pair of locations separated in a specific direction of the structure 10 are connected, when the target structure 10 vibrates in a mode in which the target structure 10 moves relative to the specific direction, a vibration system including an inertia connecting element and a spring element is coupled. Then, the inertia connecting element is relatively displaced, and the damper elements connected in parallel are relatively displaced to absorb the vibration energy.
In addition, the specifications of the viscous mass damper with spring are set corresponding to the vibration characteristics of the target structure, the response magnification of the target structure is optimized, and the vibration frequency ω corresponding to the two fixed points P and Q is Since the response magnification determined by the elastic coefficient Kb of the spring element 40 and the inertial mass mr of the inertial connection element 30 is made substantially equal at the frequency, the damper element 50 is relatively displaced along the specific direction of the inertial connection element 30. Accordingly, the vibration energy is absorbed, and the level of the relative vibration response of the pair of portions that are separated in the specific direction of the target structure 10 can be reduced.
Further, since the damping coefficient c is adjusted so that the values at the two fixed points P and Q are substantially substantially maximal, the damper element 50 has an appropriate damping coefficient c, and the inertia connecting element 30 The vibration energy is absorbed in accordance with the relative displacement along the specific direction, the amplitude, the relative displacement, or the acceleration of the target structure 10 is further reduced, and the relative relationship between the pair of locations separated in the specific direction of the target structure 10 It is possible to prevent the level of the vibration response from exceeding the response magnification corresponding to the two fixed points.
In addition, the elastic coefficient kb of the spring element is obtained from the mass ratio μ and the elastic coefficient k of the main frame, and the damping coefficient c of the damper element is determined from the mass ratio μ, the apparent inertia mass mr of the inertia connecting element, and the inherent viscosity mass damper with the spring. Since the displacement response magnification of the target structure is optimized based on the frequency ωr, the elastic coefficient Kb of the spring element and the inertia connecting element are used at frequencies near the excitation frequency ω corresponding to the two fixed points. The response magnifications determined by the inertial mass mr of the inertial connection element are substantially equal, and the damper element absorbs vibration energy along with the relative displacement along the specific direction of the inertial connection element, and the pair of locations separated in the specific direction of the target structure. The level of relative vibration response can be reduced.
In addition, the elastic coefficient kb of the spring element is obtained from the mass ratio μ and the elastic coefficient k of the main frame, and the damping coefficient c of the damper element is determined from the mass ratio μ, the apparent inertia mass mr of the inertia connecting element, and the inherent viscosity mass damper with the spring. Since the acceleration response magnification of the target structure is optimized based on the frequency ωr, the elastic coefficient Kb of the spring element and the inertia connecting element are used at frequencies near the excitation frequency ω corresponding to the two fixed points. The response magnifications determined by the inertial mass mr of the inertial connection element are substantially equal, and the damper element absorbs vibration energy along with the relative displacement along the specific direction of the inertial connection element, and the pair of locations separated in the specific direction of the target structure. The level of relative vibration response can be reduced.
A spring element made of an elastic body and a viscous mass damper 100 in which a rotating body 130 fitted to the male screw of the linear motion shaft 120 is rotatably supported and a viscous fluid 150 is sealed between the frame 140 and the rotating body 130. Since the viscous mass damper with a spring directly connected to 200 is connected to a pair of locations separated in a specific direction of the target structure 10, if the target structure 10 vibrates in a mode in which the target structure 10 moves relative to the specific direction, The vibration system composed of the mass damper 100 and the spring element 200 oscillates in combination, the linear motion shaft 120 is relatively displaced in the linear motion direction, the rotating body rotates, shear force is generated in the viscous fluid, and the viscous fluid Absorbs vibration energy.
In addition, the rotating element 130 fitted to the male screw of the linear motion shaft 120 is rotatably supported, and the viscous mass damper 100 in which the viscous fluid 150 is sealed between the frame 140 and the rotating body 130 and the spring element 200 made of a plate material. Are connected to a pair of locations separated in a specific direction of the target structure, so that the viscous mass damper is vibrated when the target structure 10 vibrates in a mode of relative movement in the specific direction. The vibration system composed of 100 and the spring element 200 oscillates, the linear motion shaft is relatively displaced in the linear motion direction, the rotating body rotates, shearing force is generated in the viscous fluid, and the viscous fluid is subjected to vibration energy. To absorb.
Further, the viscous mass damper 100 in which the rotating body 130 fitted to the male screw of the linear motion shaft 120 is rotatably supported and the viscous fluid 150 is sealed between the frame 140 and the rotating body 130 is targeted via the spring element 200. Since it is connected to the structure 10 and both ends of the linear motion shaft 120 are connected to other parts of the target structure 10, and the connected parts are arranged in a specific direction, the target structure is in a specific direction. When vibrating in the mode of relative motion, the vibration system composed of the viscous mass damper 100 and the spring element 200 vibrates, the linear motion shaft 120 is relatively displaced in the linear motion direction, the rotating body rotates, and the viscous fluid A shearing force is generated in the viscous fluid, and the viscous fluid absorbs vibration energy.
In addition, the specifications of the viscous mass damper with spring are set in accordance with the vibration characteristics of the target structure, the response magnification of the target structure 10 is optimized, and the frequency near the excitation frequency ω corresponding to the two fixed points is set. The response magnifications determined by the elastic coefficient Kb of the spring element and the inertia mass mr of the viscous mass damper are substantially equal, and the viscous mass damper absorbs vibration energy with relative displacement between the frame and the linear motion shaft, It is possible to reduce the level of relative vibration response of a pair of locations separated in a specific direction.
In addition, the damping coefficient c is adjusted so that the values at the two fixed points are substantially maximum, so that the vibration energy is absorbed along with the relative displacement of the frame and the direct coaxial, and the object is based on the support. The amplitude, relative displacement, or acceleration corresponding to the absolute displacement of the structure is made smaller, and the level of the relative vibration response of a pair of points separated in a specific direction of the support-based elephant structure is two fixed points. It is possible not to exceed the response magnification corresponding to.

  The present invention is not limited to the embodiments described above, and various modifications can be made without departing from the spirit of the invention.

It is a conceptual diagram of the seismic isolation device and the vibration damping device according to the first and fourth embodiments of the present invention. It is a conceptual diagram of the seismic isolation apparatus which concerns on 2nd embodiment of this invention. It is a conceptual diagram of the seismic isolation apparatus which concerns on 3rd embodiment of this invention. It is a conceptual diagram of the vibration damping device which concerns on 5th embodiment of this invention. It is a conceptual diagram of the vibration damping device which concerns on 6th embodiment of this invention. It is a conceptual diagram of the vibration damping device which concerns on 7th embodiment of this invention. It is a conceptual diagram of the vibration damping device which concerns on 8th embodiment of this invention. It is a conceptual diagram of the vibration damping device which concerns on 9th embodiment of this invention. It is a conceptual diagram of the vibration damping device concerning a 10th embodiment of the present invention. It is sectional drawing of the viscous mass damper which concerns on embodiment of this invention. It is a conceptual diagram of the spring element which concerns on embodiment of this invention. It is a conceptual diagram of the target structure of this invention. It is graph 1 of the frequency ratio-displacement response magnification which concerns on embodiment of this invention. It is a graph 2 of the frequency ratio-displacement response magnification which concerns on embodiment of this invention. It is a graph 3 of the frequency ratio / damping constant-mass ratio according to the embodiment of the present invention. 5 is a graph 4 of a frequency ratio / damping constant-mass ratio according to the embodiment of the present invention. It is a graph which shows the numerical analysis result of Example 1 of this invention. It is an external view of the model test apparatus of Example 2 of this invention. It is a result table | surface of the model test of Example 2 of this invention.

Explanation of symbols

DESCRIPTION OF SYMBOLS 5 Support body 6 Additional system 10 Target structure 11 Attachment part 12 Attachment part 13 Attachment part 20 Main frame 30 Inertial connection element 40 Spring element 50 Damper element 100 Viscous mass damper 110 Linear guide 120 Direct acting shaft 130 Rotating body 131 Screw nut 132 Rotating cylinder 140 Frame 141 Screw nut frame 142 Rotating cylindrical frame 143 Bearing 150 Viscous fluid 200 Spring element 210 Elastic body 220 First member 221 Flange 222 Elastic body support member 230 Second member 231 Flange 232 Elastic body support member 300 Clevis 400 Spring element 410 Plate material 411 One end 412 The other end 420 Mounting flange

Claims (2)

A seismic isolation device for isolating displacement in a specific direction of a target structure supported by a main frame on the basis of a support,
An inertia connecting element that converts the relative displacement in a specific direction into the amount of rotation of the rotating body;
A spring element that generates an elastic reaction force acting along a specific direction corresponding to a relative displacement in a specific direction;
A damper element that generates a damping resistance force acting along a specific direction corresponding to a relative speed in a specific direction;
With
A system in which the inertia connecting element and the damper element are connected in parallel and the spring element are connected in series when the structure composed of the seismic isolation device, the main frame, and the target structure is expressed as a mass point model. A springy viscous mass damper is connected between the support and the target structure,
The inertia connecting element includes a linear motion shaft provided with a male screw, a rotating body provided with a female screw fitted to the male screw, and a frame that rotatably supports the rotating body;
The damper element has a viscous fluid sealed in a gap between the inner surface of the frame and the rotating body;
The spring element has an elastic body and a first member and a second member sandwiching the elastic body,
The elastic body is a plate-like member made of a flexible material that is elastically deformed by receiving a shearing force,
The first member has a first flange and a first elastic body support member fixed to the first flange,
The second member has a second flange and a second elastic body support member fixed to the second flange,
The first elastic support member and the second elastic support member sandwich the elastic body,
When the first member and the second member move in a direction away from each other, a shearing force is generated in the elastic body, and the direction in which the first member and the second member are separated from each other coincides with a specific direction.
The linear motion direction of the linear motion shaft substantially coincides with the specific direction,
One of the frame or the linear motion shaft is connected to one of the support or the target structure,
Connecting the other of the frame or the linear motion shaft to the first member of the spring element;
Connecting the second member of the spring element to the other of the support or the target structure;
A seismic isolation device characterized by that. A vibration damping device for damping vibration accompanied by relative deformation in a specific direction of a target structure,
An inertia connecting element that converts the relative displacement in a specific direction into the amount of rotation of the rotating body;
A spring element that generates an elastic reaction force acting along a specific direction corresponding to a relative displacement in a specific direction;
A damper element that generates a damping resistance force acting along a specific direction corresponding to a relative speed in a specific direction;
With
When the structure of the vibration control device is expressed as a mass model, a viscous mass damper with a spring, which is a system in which the inertia connecting element and the damper element are connected in parallel and the spring element in series, specifies the target structure. Connected between a pair of locations separated in the direction,
The inertia connecting element includes a linear motion shaft provided with a male screw, a rotating body provided with a female screw fitted to the male screw, and a frame that rotatably supports the rotating body;
The damper element has a viscous fluid sealed in a gap between the inner surface of the frame and the rotating body;
The spring element has an elastic body and a first member and a second member sandwiching the elastic body,
The elastic body is a plate-like member made of a flexible material that is elastically deformed by receiving a shearing force,
The first member has a first flange and a first elastic body support member fixed to the first flange,
The second member has a second flange and a second elastic body support member fixed to the second flange,
The first elastic support member and the second elastic support member sandwich the elastic body,
When the first member and the second member move in a direction away from each other, a shearing force is generated in the elastic body, and the direction in which the first member and the second member are separated from each other coincides with a specific direction.
The target structure has a pair of attachment parts spaced apart in a specific direction,
The linear motion direction of the linear motion shaft substantially coincides with the specific direction,
One of the frame or the linear motion shaft is connected to one of the pair of attachment parts,
Connecting the other of the frame or the linear motion shaft to the first member of the spring element;
Connecting the second member of the spring element to the other of the pair of attachment parts;
A vibration damping device characterized by that.

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