JP5123772B2 - 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 Kenji Saito and two others, “Study on optimal response control and Kelvin model method of one-mass structure with linear viscous damper using inertial connection element”, “Structural Engineering Papers”, Architectural Institute of Japan, March 2007 May 20, VOL. 53B, P.I. 53-56 Kenji Saito, 1 other person, “A Study on Optimal Response Control of Damping Structures with Viscous Dampers Using Inertial Connection Elements -Replacement Method of Linear Viscous Elements with Equivalent Nonlinear Viscous Elements in Optimal Design System-", Nihon Architecture Academic Society Technical Report, No. 26, 2007.12 Kenji Saito, 3 others, “Vibration experiment of a single layer response control system with inertial connection element, optimized soft spring element and viscous element”, Structural Engineering Papers, Vol.54B, Architectural Institute of Japan. p.623-634, 2008.3 Kenji Saito and two others, “A Study on Response Control of Damping Structure with Viscous Damper Using Inertial Connection Elements”, Structural Engineering Papers, Vol.54B, Architectural Institute of Japan, p.635-648, 2008.3 Kenji Saito and three others, “A vibration experiment of a more optimal design system in which a linear viscous damper and a support member using an inertial connection element are connected in series (Part 1 Outline of the experiment)”, Abstracts of Annual Conference of Architectural Institute of Japan, B- 2,2007.8 Shigeki Nakanami and three others, “A vibration experiment of a more optimal design system in which a linear viscous damper using an inertia connecting element and a support member are connected in series (Part 2 Response characteristics to harmonic excitation”) , B-2, 2007.8 Hidenori Kida and three others, “A vibration experiment of a more optimal design system in which a linear viscous damper using an inertial connection element and a support member are connected in series (Part 3 Response characteristics to random vibration)”, Abstracts of Annual Conference of Architectural Institute of Japan Shu, B-2, 2007.8 Shigeki Nakanami and one other, "Vibration characteristics of a more optimal design system in which linear viscous dampers using inertia connection elements and support members are connected in series", Sumitomo Mitsui Construction Engineering Laboratory report, 2007.9

  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-mentioned object, N or more seismic isolation devices for damping the vibration of the target structure supported by the main frame based on the support according to the present invention or two or more damping devices for damping In response to the inertial connection element for converting the relative displacement in the specific direction generated by the vibration to the amount of rotation of the rotating body and the relative displacement in the specific direction. A spring element that generates an elastic reaction force acting along a specific direction and a damper element that generates a damping resistance force acting along a specific direction corresponding to a relative speed in the specific direction; A viscous mass damper, which is a system in which the damper elements are connected in parallel, and a spring element are connected in series, and the elastic mass damper with a spring specifies an elastic coefficient kb of the spring element and a method for specifying the inertia connecting element N springs each having a damper natural frequency ω corresponding to an apparent inertia mass m with respect to the relative acceleration of the vibration and a damping coefficient c corresponding to a value obtained by dividing the damping resistance of the damper element by the relative speed. The attached viscous mass dampers are attached to each of the target structures so as to be synchronously displaced relative to each other in one of the same phase or half phase in response to the relative displacement in a specific direction, and the N viscous masses with springs The dampers have different damper natural frequencies ωj (j = 1 to N).

According to the configuration of the invention, the viscous mass damper with a spring is a system in which the viscous mass damper, which is a system in which the inertia connecting element and the damper element are connected in parallel, and the spring element are connected in series. A relative displacement in a specific direction generated by vibration of the inertial connection element is converted into a 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. The damper natural frequency ω corresponds to the elastic coefficient kb of the spring element and the apparent inertia mass m with respect to the relative acceleration in a specific direction of the inertia connecting element. A damping coefficient c corresponds to a value obtained by dividing the damping resistance of the damper element by the relative speed. N said viscous mass dampers with springs are each attached to the target structure. The N viscous mass dampers with springs are displaced relative to each other in synchronism with one of the same phase or half phase corresponding to the relative displacement in a specific direction. The damper natural frequencies ωj (j = 1 to N) of the N viscous mass dampers with springs are different from each other.
As a result, the N viscous mass dampers with springs having different damper natural frequencies disperse the vibration energy of the target structure in a wider frequency band and reduce the response.

  In order to achieve the above-mentioned object, N or more seismic isolation devices for damping the vibration of the target structure supported by the main frame based on the support according to the present invention or two or more damping devices for damping A spring-mounted viscous mass damper, wherein the spring-attached viscous mass damper is provided with a linear motion shaft provided with a male screw, a rotary body provided with a female screw fitted to the male screw, and a frame for rotatably supporting the rotary body. A system having a viscous mass damper having a viscous fluid sealed in a gap between the inner surface of the frame and the rotating body and a spring element having an elastic body, wherein the viscous damper and the spring element are connected in series; The elastic coefficient kb, which is a value obtained by dividing the reaction force generated when the spring-equipped viscous mass damper displaces the spring element by a relative distance in the linear motion direction, and the linear motion of the viscous mass damper. Linear movement of axis And the viscous mass damper corresponding to the damper natural frequency ω corresponding to the apparent inertia mass m which is a value obtained by dividing the reaction force acting in the linear motion direction by the relative acceleration when the linear mass is linearly moved at a predetermined relative acceleration. And a damping coefficient c corresponding to a 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 a constant relative speed, and N springs are attached. A viscous mass damper is attached to each of the target structures so as to be displaced relative to each other in the linear motion direction in synchronization with one of the same phase or half phase corresponding to the relative displacement in a specific direction. The damper natural frequencies ωj (j = 1 to N) of the viscous mass damper with a spring are different from each other.

According to the configuration of the invention, the viscous mass damper with a spring is a system in which the viscous damper and the spring element are connected in series. 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 rotatably supporting the rotating body, an inner surface of the frame, and a gap between the rotating body With viscous fluid enclosed in The spring element has an elastic body. The damper natural frequency ω 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 by the relative distance, and the linear motion of the viscous mass damper. This corresponds to the apparent inertia mass m which is a value obtained by dividing the reaction force acting in the linear motion direction by the relative acceleration when the shaft is linearly moved in the linear motion direction at a predetermined relative acceleration. The damping coefficient c corresponds to a value obtained by dividing a reaction force acting in the linear motion direction by the linear velocity when the linear motion shaft of the viscous mass damper is linearly moved at a constant relative velocity. N said viscous mass dampers with springs are each attached to the target structure. The N viscous mass dampers with springs are displaced relative to each other in the linear motion direction in synchronism with one of the same phase or half phase corresponding to the relative displacement in a specific direction. The damper natural frequencies ωj (j = 1 to N) of the N viscous mass dampers with springs are different from each other.
As a result, the N viscous mass dampers with springs having different damper natural frequencies disperse the vibration energy of the target structure in a wider frequency band and reduce the response.

  Below, the seismic isolation apparatus or damping device 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.

Further, in the seismic isolation device or the vibration damping device according to the embodiment of the present invention, the N damper natural frequencies ωj (j = 1 to N) substantially coincide with the N optimum tuning frequencies, respectively, Thus, when it is assumed that each of the damper natural frequencies ωj (j = 1 to N) of the N viscous mass dampers with springs matches the N optimum tuning frequencies, the excitation frequency p When the horizontal axis is the ratio p / ωs of the natural frequency ωs of the vibration mode displaced in a specific direction of the system composed of the main frame and the target structure, and the vertical axis is the response magnification of the target structure, On the line indicating the response magnification, the values at at least (N + 1) fixed points that are constant regardless of the values of the respective damping coefficients c of the N viscous mass dampers with springs are substantially equal. The response magnification is the vibration when the target structure is forcibly vibrated. The dynamic response magnification, which is the ratio of the static displacement of the target structure due to vibration and the amplitude of the target structure that vibrates in response This is one of the displacement response magnification, which is the ratio to the displacement of the object, or the acceleration response magnification, which is the ratio of the acceleration of the object that vibrates in response to the acceleration of the support when the support is forcibly vibrated. .
With the configuration of the embodiment according to the present invention, the N damper natural frequencies ωj (j = 1 to N) substantially coincide with the N optimum tuning frequencies, respectively. The ratio p / ωs between the vibration frequency p and the natural frequency ωs of the vibration mode displaced in a specific direction of the system composed of the main frame and the target structure is taken as the horizontal axis, and the response magnification of the target structure is taken as the vertical axis. The value at at least (N + 1) fixed points that are constant regardless of the value of the damping coefficient c of each of the N viscous mass dampers with springs on the line indicating the response magnification. Are substantially equal. The response magnification is one of a dynamic response magnification, a displacement response magnification, or an acceleration response magnification. The dynamic response magnification is a ratio between the static displacement of the target structure due to the excitation force when the target structure is forcedly excited and the amplitude of the target structure that vibrates in response. The displacement response magnification is a ratio between the displacement of the support when the support is forcibly excited and the displacement of the target structure that vibrates in response. The acceleration response magnification 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.
As a result, since the values at the (N + 1) fixed points are equal, the response magnifications near the frequencies corresponding to the (N + 1) fixed points can be equalized, and the peak response magnification can be lowered.

Furthermore, in the seismic isolation device or the vibration damping device according to the embodiment of the present invention, the N attenuation coefficients c are values that substantially match the N optimal attenuation coefficients, respectively, where the N attenuation coefficients Assuming that the coefficient c matches the N optimum attenuation coefficients, the values at the (N + 1) fixed points are substantially substantially maximal.
With the configuration of the embodiment according to the invention, the N attenuation coefficients cj (j = 1 to N) substantially match the N optimum attenuation coefficients, respectively. The value at the (N + 1) fixed points is substantially substantially maximum for each.
As a result, the response magnification at the (N + 1) fixed points becomes a peak having a maximum value, and the response magnification at the peak can be adjusted to the overall response magnification.

Furthermore, in the seismic isolation device or the vibration damping device according to the embodiment of the present invention, the N damper natural frequencies ωj (j = 1 to N) substantially match the N optimum tuning frequencies, respectively, Thus, when it is assumed that each of the damper natural frequencies ωj (j = 1 to N) of the N viscous mass dampers with springs matches the N optimum tuning frequencies, the excitation frequency p When the horizontal axis is the ratio p / ωs of the natural frequency ωs of the vibration mode displaced in a specific direction of the system composed of the main frame and the target structure, and the vertical axis is the response magnification of the target structure, The variation of each response magnification at the (N + 1) peak points having the maximum value on the line indicating the response magnification falls within a predetermined range, and the response magnification is obtained when the target structure is forcibly excited. The target structure vibrated in response to the static displacement of the target structure due to the excitation force Dynamic response magnification, which is the ratio to the amplitude, displacement response magnification, which is the ratio of the displacement of the support when the support is forced to vibrate and the displacement of the target structure that vibrates in response, or the support is forced This is one of the acceleration response magnifications, which is the ratio between the acceleration of the support when shaken and the acceleration of the object that vibrates in response.
With the configuration of the embodiment according to the present invention, the N damper natural frequencies ωj (j = 1 to N) substantially coincide with the N optimum tuning frequencies, respectively. The ratio p / ωs between the vibration frequency p and the natural frequency ωs of the vibration mode displaced in a specific direction of the system composed of the main frame and the target structure is taken as the horizontal axis, and the response magnification of the target structure is taken as the vertical axis. Then, the variation of each response magnification at the (N + 1) peak points having the maximum value on the line indicating the response magnification falls within a predetermined range.
The response magnification is one of a dynamic response magnification, a displacement response magnification, or an acceleration response magnification. The dynamic response magnification is a ratio between the static displacement of the target structure due to the excitation force when the target structure is forcedly excited and the amplitude of the target structure that vibrates in response. The displacement response magnification is a ratio between the displacement of the support when the support is forcibly excited and the displacement of the target structure that vibrates in response. The acceleration response magnification 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.
As a result, the variation of the response magnification at the (N + 1) peak points having the maximum value falls within the predetermined range, and the response magnification near the peak point can be made uniform.

Furthermore, in the seismic isolation device or the vibration damping device according to the embodiment of the present invention, the N attenuation coefficients cj (j = 1 to N) are values that substantially match the N optimal attenuation coefficients, respectively, Then, it is assumed that each of the damping coefficients cj (j = 1 to N) of the N pieces of the viscous mass dampers with springs corresponds to the N optimum damping coefficients, respectively. The average value of the respective response magnifications at the N peak points having the maximum values above becomes substantially minimum.
With the configuration of the embodiment according to the invention, the N attenuation coefficients cj (j = 1 to N) substantially coincide with the N optimum attenuation coefficients, respectively. On the line indicating the response magnification, the average value of the response magnifications at the N peak points is substantially minimum.
As a result, the response magnification in the vicinity of the peak can be lowered within a range in which the variation of each response magnification at the (N + 1) peak points having the maximum value falls within a predetermined range.

Furthermore, in the seismic isolation device or the vibration damping device according to the embodiment of the present invention, the N damper natural frequencies ωj (j = 1 to N) substantially match the N optimum tuning frequencies, respectively, Thus, when it is assumed that each of the damper natural frequencies ωj (j = 1 to N) of the N viscous mass dampers with springs matches the N optimum tuning frequencies, the excitation frequency p When the horizontal axis is the ratio p / ωs of the natural frequency ωs of the vibration mode displaced in a specific direction of the system composed of the main frame and the target structure, and the vertical axis is the response magnification of the target structure, The average value of the response magnifications at the N peak points having a minimum value on the line indicating the response magnification is substantially minimum, and the response magnification is determined by exciting the target structure. The ratio between the static displacement of the target structure due to force and the amplitude of the target structure oscillated in response. Dynamic response magnification, displacement response magnification, which is the ratio of displacement of the support when the support is forcibly vibrated and displacement of the target structure that vibrates in response, or support when the support is forcibly vibrated This is one of the acceleration response magnifications, which is the ratio between the acceleration of the object and the acceleration of the object that vibrates in response.
With the configuration of the embodiment according to the invention, the N damper natural frequencies ωj (j = 1 to N) substantially match the N optimum tuning frequencies with the optimum tuning frequencies. The ratio p / ωs between the vibration frequency p and the natural frequency ωs of the vibration mode displaced in a specific direction of the system composed of the main frame and the target structure is taken as the horizontal axis, and the response magnification of the target structure is taken as the vertical axis. Then, the average value of each response magnification at N peak points having a minimum value on the line indicating the response magnification is substantially the minimum. The response magnification is one of a dynamic response magnification, a displacement response magnification, or an acceleration response magnification. The dynamic response magnification is a ratio between the static displacement of the target structure due to the excitation force when the target structure is forcedly excited and the amplitude of the target structure that vibrates in response. The displacement response magnification is a ratio between the displacement of the support when the support is forcibly excited and the displacement of the target structure that vibrates in response. The acceleration response magnification 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.
As a result, the average value of the response magnifications at the N peak points having the minimum value is substantially minimized, the response magnification near the N peak points can be lowered, and the overall response magnification can be lowered.

Furthermore, in the seismic isolation device or the vibration damping device according to the embodiment of the present invention, the N damper natural frequencies ωj (j = 1 to N) substantially match the N optimum tuning frequencies, respectively, Thus, when it is assumed that each of the damper natural frequencies ωj (j = 1 to N) of the N viscous mass dampers with springs matches the N optimum tuning frequencies, the excitation frequency p When the horizontal axis is the ratio p / ωs of the natural frequency ωs of the vibration mode displaced in a specific direction of the system composed of the main frame and the target structure, and the vertical axis is the response magnification of the target structure, On the line indicating the response magnification, the average of the response magnification at the excitation frequency p of a predetermined width is substantially minimum, and the response magnification is the target structure by the excitation force when the target structure is forcibly excited. Dynamic response multiplication, which is the ratio between the static displacement of an object and the amplitude of the target structure oscillated in response , Displacement response magnification, which is the ratio of the displacement of the support body when the support body is forced to vibrate and the displacement of the target structure that vibrates in response, or the acceleration and response of the support body when the support body is forced This is one of the acceleration response magnifications that is a ratio with the acceleration of the object that vibrates.
With the configuration of the embodiment according to the present invention, the N damper natural frequencies ωj (j = 1 to N) substantially coincide with the N optimum tuning frequencies, respectively. The ratio p / ωs between the vibration frequency p and the natural frequency ωs of the vibration mode displaced in a specific direction of the system composed of the main frame and the target structure is taken as the horizontal axis, and the response magnification of the target structure is taken as the vertical axis. In this case, the average of the response magnifications at the excitation frequency p having a predetermined width on the line indicating the response magnifications is substantially minimum. The response magnification is one of a dynamic response magnification, a displacement response magnification, or an acceleration response magnification. The dynamic response magnification is a ratio between the static displacement of the target structure due to the excitation force when the target structure is forcedly excited and the amplitude of the target structure that vibrates in response. The displacement response magnification is a ratio between the displacement of the support when the support is forcibly excited and the displacement of the target structure that vibrates in response. The acceleration response magnification 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.
As a result, the average response magnification at the excitation frequency p having a predetermined width is substantially minimized, and the response magnification in the vicinity of the excitation frequency p having a predetermined width can be lowered.

Furthermore, the seismic isolation device or the vibration damping device according to the embodiment of the present invention has an optimal number of N damper natural frequencies ωj, which is the lower of the N damper natural frequencies ωj (j = 1 to N). The value is lower than the lower optimal tuning frequency among the tuning frequencies, and the higher of the N damper natural frequencies ωj (j = 1 to N), the higher damper natural frequency ωj. Approximately equal to or slightly deviates from the higher one of the optimum tuning frequencies, where each of the damper natural frequency ωj (j = 1 to 1) of the N viscous mass dampers with springs is provided. N) is assumed to be equal to each of the N optimally tuned frequencies, and the natural frequency ωs of the vibration mode that is displaced in a specific direction of the system composed of the excitation frequency p, the main frame, and the target structure. Response of the target structure with the ratio p / ωs to the horizontal axis When the rate is the vertical axis, the value of N damping coefficients c, which is a value obtained by dividing the damping resistance force of the N damper elements by the relative speed on the line indicating the response magnification, is considered. The values at (N + 1) fixed points that are constant values are substantially equal,
The response magnification is a dynamic response magnification, which is a ratio between the static displacement of the target structure due to the excitation force when the target structure is forcedly vibrated and the amplitude of the target structure that vibrates in response. Vibration in response to the displacement response magnification, which is the ratio of the displacement of the support when it 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 to the acceleration of the target object.
According to the configuration of the embodiment according to the invention, the lower damper natural frequency ωj among the N damper natural frequencies ωj (j = 1 to N) is the lower of the N optimum tuning frequencies. This value is lower than the optimum tuning frequency. Of the N damper natural frequencies ωj (j = 1 to N), the higher damper natural frequency ωj substantially coincides with the higher optimal tuning frequency of the N optimum tuning frequencies. Or it shifts slightly. When it is assumed that each of the damper natural frequencies ωj (j = 1 to N) of the N viscous mass dampers with springs matches the N optimum tuning frequencies, the excitation frequency p and the main frame When the ratio p / ωs to the natural frequency ωs of the vibration mode displaced in a specific direction of the system composed of the target structure is the horizontal axis and the response magnification of the target structure is the vertical axis, the response magnification (N + 1) fixed points that are constant regardless of the value of N damping coefficients c, which is a value obtained by dividing the damping resistance force of the N damper elements by the relative speed. The values at are approximately equal. The response magnification is one of a dynamic response magnification, a displacement response magnification, or an acceleration response magnification. The dynamic response magnification is a ratio between the static displacement of the target structure due to the excitation force when the target structure is forcedly excited and the amplitude of the target structure that vibrates in response. The displacement response magnification is a ratio between the displacement of the support when the support is forcibly excited and the displacement of the target structure that vibrates in response. The acceleration response magnification 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.
As a result, it is possible to adjust the response magnification by equalizing the response magnification in the vicinity of the frequency corresponding to the (N + 1) fixed points.

Furthermore, the seismic isolation device or the vibration damping device according to the embodiment of the present invention has an optimal number of N damper natural frequencies ωj, which is the lower of the N damper natural frequencies ωj (j = 1 to N). The value is lower than the lower optimal tuning frequency of the tuning frequencies, where each of the damper natural frequencies ωj (j = 1 to N) of the N viscous mass dampers with springs is The ratio between the vibration frequency p and the natural frequency ωs of the vibration mode displaced in a specific direction of the system composed of the main frame and the target structure when it is assumed that each of the N optimally tuned frequencies corresponds. When p / ωs is the horizontal axis and the response magnification of the target structure is the vertical axis, the damping resistance force of the N damper elements is divided by the relative speed on the line indicating the response magnification. Regardless of the value of a certain N attenuation coefficients c, The values at the (N + 1) fixed points are substantially equal, and the response magnification is the target structure that vibrates in response to the static displacement of the target structure due to the excitation force when the target structure is forcibly excited. Dynamic response magnification, which is the ratio to the amplitude of the object, displacement response magnification, which is the ratio of the displacement of the support when the support is forced to vibrate and the displacement of the target structure that vibrates in response, or the support This is one of the acceleration response magnifications, which is the ratio between the acceleration of the support when forcedly excited and the acceleration of the object that vibrates in response.
According to the configuration of the embodiment according to the invention, the lower damper natural frequency ωj among the N damper natural frequencies ωj (j = 1 to N) is the lower of the N optimum tuning frequencies. This value is lower than the optimum tuning frequency. When it is assumed that each of the damper natural frequencies ωj (j = 1 to N) of the N viscous mass dampers with springs matches the N optimum tuning frequencies, the excitation frequency p and the main frame When the ratio p / ωs to the natural frequency ωs of the vibration mode displaced in a specific direction of the system composed of the target structure is the horizontal axis and the response magnification of the target structure is the vertical axis, the response magnification (N + 1) fixed points that are constant regardless of the value of N damping coefficients c, which is a value obtained by dividing the damping resistance force of the N damper elements by the relative speed. The values at are approximately equal. The response magnification is one of a dynamic response magnification, a displacement response magnification, or an acceleration response magnification. The dynamic response magnification is a ratio between the static displacement of the target structure due to the excitation force when the target structure is forcedly excited and the amplitude of the target structure that vibrates in response. The displacement response magnification is a ratio between the displacement of the support when the support is forcibly excited and the displacement of the target structure that vibrates in response. The acceleration response magnification 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.
As a result, the response magnification can be adjusted by equalizing the response magnification in the vicinity where the lower side is expanded to the lower side compared to the frequencies corresponding to (N + 1) fixed points.

Further, the seismic isolation device or the vibration damping device according to the embodiment of the present invention includes the N damper natural frequencies ωj (j = 1 to N), the higher of the N damper natural frequencies ωj. It is a value that is higher than the optimum tuning frequency, which is the higher of the optimum tuning frequencies, where each of the damper natural frequencies ωj (j = 1 to N) of the N viscous mass dampers with springs. ) And the natural frequency ωs of the vibration mode that is displaced in a specific direction of the system composed of the main frame and the target structure, When the ratio p / ωs of the horizontal axis is the horizontal axis and the response magnification of the target structure is the vertical axis, the damping resistance force of the N damper elements is divided by the relative speed on the line indicating the response magnification. Regardless of the value of the N damping coefficients c The values at (N + 1) fixed points, which are constant values, are substantially equal, and the response magnification vibrates in response to the static displacement of the target structure due to the excitation force when the target structure is forcibly excited. A dynamic response magnification that is a ratio to the amplitude of the target structure, a displacement response magnification that is a ratio of the displacement of the support structure and the displacement of the target structure that has vibrated in response to the forced excitation of the support structure, or This is one of the acceleration response magnifications, which is the ratio between the acceleration of the support when the support is forcibly excited and the acceleration of the object that vibrates in response.
According to the configuration of the embodiment according to the present invention, the higher damper natural frequency ωj of the N damper natural frequencies ωj (j = 1 to N) is the higher of the N optimum tuning frequencies. This value is higher than the optimum tuning frequency. When it is assumed that each of the damper natural frequencies ωj (j = 1 to N) of the N viscous mass dampers with springs matches the N optimum tuning frequencies, the excitation frequency p and the main frame When the ratio p / ωs to the natural frequency ωs of the vibration mode displaced in a specific direction of the system composed of the target structure is the horizontal axis and the response magnification of the target structure is the vertical axis, the response magnification (N + 1) fixed points that are constant regardless of the value of N damping coefficients c, which is a value obtained by dividing the damping resistance force of the N damper elements by the relative speed. The values at are approximately equal. The response magnification is one of a dynamic response magnification, a displacement response magnification, or an acceleration response magnification. The dynamic response magnification is a ratio between the static displacement of the target structure due to the excitation force when the target structure is forcedly excited and the amplitude of the target structure that vibrates in response. The displacement response magnification is a ratio between the displacement of the support when the support is forcibly excited and the displacement of the target structure that vibrates in response. The acceleration response magnification 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.
As a result, the response magnification can be adjusted by equalizing the response magnification in the vicinity where the lower side has expanded to the higher side compared to the frequencies corresponding to (N + 1) fixed points.

Furthermore, in the seismic isolation device or the vibration damping device according to the embodiment of the present invention, the N attenuation coefficients c substantially match the N optimum attenuation coefficients, where the N attenuation coefficients c are N. (N + 1) values at the fixed points are substantially substantially maximal for each of the above-mentioned optimum attenuation coefficients.
With the configuration of the embodiment according to the invention, the N attenuation coefficients c substantially match the N optimal attenuation coefficients. The value at the (N + 1) fixed points is substantially substantially maximum for each.
As a result, the response magnification in the vicinity of (N + 1) fixed points becomes a peak point having a maximum value, and the overall response magnification can be adjusted to the response magnification at the peak point.

Furthermore, in the seismic isolation device or the vibration damping device according to the embodiment of the present invention, the damper natural frequency ωj of each of the N damper natural frequencies ωj (j = 1 to N) is set to N predetermined values. Assuming that the N damper natural frequencies ωj (j = 1 to N) correspond to N predetermined values, respectively, the natural frequency ωs is the maximum and minimum natural frequency ωmin. The maximum value Pmax on the line indicating the response magnification when taking a value between the natural frequency ωmax is lower than the maximum value Pmax when the natural frequency ωs is the minimum natural frequency ωmin, and the natural frequency The frequency ωs is lower than the maximum value Pmax when it is the maximum natural frequency ωmax.
With the configuration of the embodiment according to the invention, the damper natural frequency ωj of each of the N damper natural frequencies ωj (j = 1 to N) substantially matches the N predetermined values. When the maximum value Pmax on the line indicating the response magnification assumes that the natural frequency ωs continuously changes between the minimum natural frequency ωmin and the maximum natural frequency ωmax, the natural frequency ωs is Lower than the maximum value Pmax when the minimum natural frequency ωmin, and lower than the maximum value Pmax when the natural frequency ωs is the maximum natural frequency ωmax,
As a result, when the natural frequency ωs of the vibration mode displaced in a specific direction of the system composed of the main frame and the target structure is changed, the change in the response magnification can be adjusted.

Furthermore, the seismic isolation device or the vibration damping device according to the embodiment of the present invention is provided with a first spring having N pieces of viscous mass dampers with first springs, which is N pieces of viscous mass dampers with springs. A viscous mass damper set with a second spring, and N viscous mass dampers with N second springs, which are N or more viscous mass dampers with springs;
The damper natural frequencies ωj (j = 1 to N) of the N first spring-equipped viscous mass dampers are different from each other, and the damper natural frequencies ωj (j = 1) of the N second viscous mass dampers with the springs ˜N) are different from each other, the damping coefficients cj (j = 1 to N) of the N first spring-attached viscous mass dampers are different from each other, and the damping coefficients cj (j = 1) of the N second spring-attached viscous mass dampers. N) are different from each other, the damper natural frequency ωj (j = 1 to N) of each of the N first viscous mass dampers with the spring and the each of the N second viscous mass dampers with the second spring. The damper natural frequency ωj (j = 1 to N) substantially matches every pair, and the damping coefficient cj (j = j = N) of each of the N first spring-equipped viscous mass dampers (j = 1 to N). 1 to N) and N pieces of viscous mass dampers with the second spring ( = 1 to N) of the respective damping coefficients cj (j = 1 to N) approximately coincide with each other, and N first viscous mass dampers with a first spring and N second viscous mass dampers with a second spring, N is such that each pair is point-symmetric with respect to the rigid center of the target structure, or so that each pair is line-symmetric with respect to a virtual line that passes through the rigid core of the symmetrical structure. A plurality of viscous mass dampers with first springs and N second viscous mass dampers with springs are respectively attached between the support and the target structure or inside the target structure.
According to the configuration of the embodiment of the present invention, the first spring-equipped viscous mass dampers are N pieces of the first spring-equipped viscous mass dampers. A set of viscous mass dampers with second springs has N number of viscous mass dampers with second springs, which is N or more of the above-mentioned N viscous mass dampers with springs. The damper natural frequency ωj (j = 1 to N) of the N first viscous mass dampers with springs is different from each other. The damper natural frequency ωj (j = 1 to N) of the N first viscous mass dampers with springs is different from each other. The N second viscous mass dampers with springs have different damper natural frequencies ωj (j = 1 to N). The damping coefficients cj (j = 1 to N) of the N first viscous mass dampers with springs are different from each other, and the damping coefficients cj (j = 1 to N) of the N second viscous mass dampers with springs are different from each other, The damper natural frequency ωj (j = 1 to N) of each of the N number of viscous mass dampers with the first spring and the damper natural frequency ωj (j of each of the N number of viscous mass dampers with the second spring) = 1 to N) approximately matches every pair. The damping coefficient cj (j = 1 to N) of each of the N first viscous mass dampers with springs (j = 1 to N) and the N viscous mass dampers with second springs (j = 1 to N) ) Substantially coincides with each other for each pair of attenuation coefficients cj (j = 1 to N). N pieces of viscous mass dampers with first springs and N pieces of viscous mass dampers with second springs are symmetric with respect to each other with respect to the rigid center of the target structure, or the rigidity of the target structure. N pieces of viscous mass dampers with first springs and N pieces of viscous mass dampers with second springs are used as a support and target structure so that each pair is symmetrical with respect to a virtual line passing through the center. Or within each of the target structures.
As a result, torsional motion induction can be suppressed in the system composed of the main frame and the target structure due to the reaction force of the viscous mass damper with spring, and the energy that induces torsional vibration can be isolated or controlled.

Furthermore, the seismic isolation device or the vibration damping device according to the embodiment of the present invention includes a plurality of sets of spring-attached viscous mass damper sets each having two or more N pieces of spring-attached viscous mass dampers,
The damper natural frequency ωj (j = 1 to N) of the N viscous mass dampers with springs belonging to the same set of viscous mass dampers with springs is different, and belongs to the same set of viscous mass dampers with springs. The damping coefficients cj (j = 1 to N) of N pieces of the viscous mass dampers with springs are different from each other, and are different from the whole of the N pieces of viscous mass dampers with springs belonging to a plurality of viscous mass damper sets with springs. The damper natural frequency ωj (j = 1 to N) of each of the plurality of spring-attached viscous mass dampers selected and combined with one spring-attached viscous mass damper belonging to the set substantially coincides with each other, and Select and combine one spring-attached viscous mass damper belonging to a different group from the whole of the N spring-attached viscous mass dampers belonging to the spring-attached viscous mass damper set. The damping coefficients cj (j = 1 to N) of each of the plurality of spring-attached viscous mass dampers substantially match each other, and each of the N spring-attached viscous mass dampers belonging to different sets of spring-attached viscous mass damper sets. With N springs each belonging to a plurality of sets of viscous mass dampers with springs so that each rotational moment acting around the rigid core of the target structure cancels each other by the reaction force generated by Viscous mass dampers are respectively attached between the support and the target structure or inside the target structure.
With the configuration of the embodiment according to the invention, a plurality of sets of viscous mass dampers with springs each include two or more N viscous mass dampers with springs. The damper natural frequency ωj (j = 1 to N) of the N viscous mass dampers with springs belonging to the same set of viscous mass dampers with springs is different. The damping coefficients cj (j = 1 to N) of the N viscous mass dampers with a spring belonging to the same set of viscous mass dampers with a spring are different from each other. A plurality of the above-mentioned spring-attached viscous mass dampers obtained by selecting and combining one spring-attached viscous mass damper belonging to a different group from the whole of the above-mentioned N pieces of spring-attached viscous mass dampers belonging to a plurality of spring-attached viscous mass damper sets. Each of the damper natural frequencies ωj (j = 1 to N) substantially coincides with each other. A plurality of the above-mentioned spring-attached viscous mass dampers obtained by selecting and combining one spring-attached viscous mass damper belonging to a different group from the whole of the above-mentioned N pieces of spring-attached viscous mass dampers belonging to a plurality of spring-attached viscous mass damper sets. Each of the attenuation coefficients cj (j = 1 to N) substantially matches each other. Each rotational moment acting around the rigid core of the target structure is canceled out by each group by the reaction force generated by each of N spring mass viscous dampers belonging to different sets of spring mass viscous dampers. In this way, each of N spring-loaded viscous mass dampers belonging to a plurality of sets of spring-attached viscous mass damper sets is attached between the support and the target structure or inside the target structure.
As a result, torsional motion induction can be suppressed in the system composed of the main frame and the target structure due to the reaction force of the viscous mass damper with spring, and the energy that induces torsional vibration can be isolated or controlled.

As described above, the seismic isolation device according to the present invention has the following effects due to its configuration.
A system in which a viscous mass damper, which is a system in which an inertial connection element that converts relative displacement in a specific direction generated by vibration into a rotation amount of a rotating body and the damper element are connected in parallel, and the spring element are connected in series. A plurality of the viscous mass dampers with springs are prepared, and the plurality of viscous mass dampers with springs are respectively attached to the target structure, and each of the damper natural frequencies ωj (j = 1) of the plurality of viscous mass dampers with springs is provided. Since N) are different from each other, the N viscous mass dampers with springs having different damper natural frequencies disperse the vibration energy of the target structure in a wider frequency band and reduce the response.
With a spring that is a system in which the spring element is connected in series with a viscous mass damper composed of a linear motion shaft, a rotating body screwed into the linear motion shaft, and a viscous fluid sealed in a gap between the rotational body and the frame A plurality of viscous mass dampers are prepared, a plurality of the above-mentioned spring-attached viscous mass dampers are attached to the target structure, and the damper natural frequency ωj (j = 1 to N) of each of the plurality of spring-attached viscous mass dampers is Since they are made different from each other, the N viscous mass dampers with springs having different damper natural frequencies disperse the vibration energy of the target structure in a wider frequency band and reduce the response.

Further, when the horizontal axis is p / ωs and the vertical axis is the response magnification of the target structure, the values of the respective damping coefficients c of the plurality of the spring-attached viscous mass dampers on the line indicating the response magnification are shown. The N damper natural frequencies ωj (j = 1 to N) are set so that the values at at least (N + 1) fixed points, which are constant values, are almost equal, so (N + 1) Since the values at the fixed points are equal, it is possible to equalize the response magnifications in the vicinity of the frequencies corresponding to the (N + 1) fixed points, and to reduce the peak response magnification.
In addition, since the N attenuation coefficients c are set so that the values at the (N + 1) fixed points are substantially maximum, the response magnification at the (N + 1) fixed points is the maximum. It becomes a peak with a value, and the overall response magnification can be adjusted.

In addition, when p / ωs is the horizontal axis and the response magnification of the target structure is the vertical axis, each response magnification at each of (N + 1) peak points having a maximum value on the line indicating the response magnification is shown. Since the N damper natural frequencies ωj (j = 1 to N) are set so that the variation falls within a predetermined range, each response magnification at the (N + 1) peak points having the maximum value is set. Variation within the predetermined range, and the response magnification near the peak point can be adjusted.
Further, the N attenuation coefficients cj (j = 1 to N) are set so that the average value of each response magnification at the N peak points having the maximum value on the line indicating the response magnification is substantially minimum. Therefore, the response magnification in the vicinity of the peak can be adjusted in a range in which the variation of each response magnification at the (N + 1) peak points having the maximum value falls within a predetermined range.
Further, when p / ωs is the horizontal axis and the response magnification of the target structure is the vertical axis, the average value of each response magnification at N peak points having a minimum value on the line indicating the response magnification. N damper natural frequencies ωj (j = 1 to N) are set such that the average value of the response magnifications at the N peak points having a minimum value is set. The response magnification in the vicinity of N peak points can be lowered, and the overall response magnification can be adjusted.
When the horizontal axis is p / ωs and the vertical axis is the response magnification of the target structure, the average of the continuous response magnifications at the excitation frequency p of a predetermined width on the line indicating the response magnification is approximately. Since the N damper natural frequencies ωj (j = 1 to N) are set so as to be minimized, the average of continuous response magnifications at the excitation frequency p of a predetermined width is substantially minimized, The response magnification in the vicinity of the excitation frequency p having a predetermined width can be adjusted.

Further, when the horizontal axis is p / ωs and the vertical axis is the response magnification of the target structure, the damping resistance force of the N damper elements is divided by the relative speed on the line indicating the response magnification. N damper natural vibrations rather than N optimal tuning frequencies where the values at (N + 1) fixed points that are constant values are substantially equal regardless of the value of N damping coefficients c that are values. Of the number ωj (j = 1 to N), the lower damper natural frequency ωj is set to a lower value, and the higher of the N damper natural frequencies ωj (j = 1 to N). Since the damper natural frequency ωj is set to a substantially coincident value, it is possible to adjust the response magnification by equalizing the response magnification in the vicinity of the frequency corresponding to the (N + 1) fixed points.
Further, when the horizontal axis is p / ωs and the vertical axis is the response magnification of the target structure, the damping resistance force of the N damper elements is divided by the relative speed on the line indicating the response magnification. N damper natural vibrations rather than N optimal tuning frequencies where the values at (N + 1) fixed points that are constant values are substantially equal regardless of the value of N damping coefficients c that are values. Of the number ωj (j = 1 to N), the lower damper natural frequency ωj is set to a lower value, and the higher of the N damper natural frequencies ωj (j = 1 to N). Since the damper natural frequency ωj is set to a substantially coincident value, the response magnification in the vicinity where the lower side has spread to the lower side compared to the frequency corresponding to (N + 1) fixed points is made equal, and the response magnification is set. Can be adjusted.
Further, when the horizontal axis is p / ωs and the vertical axis is the response magnification of the target structure, the damping resistance force of the N damper elements is divided by the relative speed on the line indicating the response magnification. N damper natural vibrations rather than N optimal tuning frequencies where the values at (N + 1) fixed points that are constant values are substantially equal regardless of the value of N damping coefficients c that are values. Of the number ωj (j = 1 to N), the higher damper natural frequency ωj is set to a higher value, and the higher of the N damper natural frequencies ωj (j = 1 to N). Since the damper natural frequency ωj is set to a substantially coincident value, the response magnification in the vicinity where the lower side spreads higher than the frequency corresponding to the (N + 1) fixed points is made equal, and the response magnification is set. Can be adjusted.
In addition, since the N attenuation coefficients c are set so that the values at the (N + 1) fixed points are substantially maximum, the response magnification at the (N + 1) fixed points is the maximum. It becomes a peak having a value, and the response magnification at the peak can be adjusted to the overall response magnification.

  The maximum value Pmax on the line indicating the response magnification when the natural frequency ωs takes a value between the minimum natural frequency ωmin and the maximum natural frequency ωmax is the minimum natural frequency ωs. The N damper natural frequencies ωj (j = 1) so as to be lower than the maximum value Pmax when the frequency is ωmin and lower than the maximum value Pmax when the natural frequency ωs is the maximum natural frequency ωmax. ~ N) is set, it is possible to adjust the change in the response magnification when the natural frequency ωs of the vibration mode displaced in a specific direction of the system composed of the main frame and the target structure changes.

Further, each of the first spring-attached viscous mass dampers having the spring-like viscous mass dampers having the same specifications, and each of the N second spring-attached viscous mass damper sets are provided. Are arranged symmetrically with respect to the centroid of the symmetrical structure, and the rotational moments around the rigid core are offset each other. The
As a result, torsional motion induction can be suppressed in the system composed of the main frame and the target structure due to the reaction force of the viscous mass damper with spring, and the energy that induces torsional vibration can be isolated or controlled.
In addition, the rotational moment around the rigid core generated by the reaction force generated by the N spring mass viscous dampers belonging to each of the plurality of spring mass viscous dampers to which the spring mass viscous dampers whose specifications match each other belongs. A plurality of spring mass viscous dampers are attached between the support and the target structure or inside the target structure so as to cancel each other.
As a result, torsional motion induction can be suppressed in the system composed of the main frame and the target structure due to the reaction force of the viscous mass damper with spring, and the energy that induces torsional vibration can be isolated or controlled.
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, a seismic isolation device or a vibration damping device according to an embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a conceptual diagram of the seismic isolation device / damping device according to an embodiment of the present invention.

The seismic isolation device is a device for isolating the vibration of the target structure supported by the main frame on the basis of the support. For example, the seismic isolation device is attached to the support and the target structural band, and makes it difficult to transmit the vibration of the support to the target structure.
The vibration damping device is a device for damping the vibration of the target structure supported by the main frame on the basis of the support. For example, the vibration damping device is attached to the target structure and suppresses the vibration level of the target structure that vibrates.

The seismic isolation device or the vibration damping device is provided with N or more spring-loaded viscous mass dampers.
N viscous mass dampers with springs are attached to each of the target structures so as to be displaced relative to each other synchronously in one of the same phase or half phase corresponding to the relative displacement in a specific direction.
For example, if both ends of the N spring mass viscous dampers are fixed to a structure that can be regarded as a rigid body, the N mass viscous spring dampers are either in phase or half phase corresponding to the relative displacement in a specific direction. In sync with each other.
The elastic mass damper with a spring is an inertial connection element that converts the relative displacement in a specific direction caused by vibration into the amount of rotation of the rotating body, and an elastic reaction force that acts along the specific direction in response to the relative displacement in the specific direction. Viscosity is a system in which an inertial connection element and a damper element are connected in parallel with a spring element that generates vibration and a damper element that generates a damping resistance acting along a specific direction corresponding to a relative speed in a specific direction. This is a system in which a mass damper and a spring element are connected in series.
The viscous mass damper with a spring has a damper natural frequency ω corresponding to the elastic coefficient kb of the spring element and the apparent inertia mass m with respect to the relative acceleration in a specific direction of the inertia connecting element and the damping resistance of the damper element. And a damping coefficient c corresponding to a value obtained by dividing force by relative speed.
The damper natural frequency ωj (j = 1 to N) of the N viscous mass dampers with springs is different from each other.

The seismic isolation device or damping device is composed of N or more spring-loaded viscous mass dampers.
N viscous mass dampers with springs are respectively attached to the target structures so as to be displaced relative to each other in the linear motion direction in synchronism with one of the same phase or half phase corresponding to the relative displacement in a specific direction.
A viscous mass damper with a spring comprises 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 rotating body. The system includes a viscous mass damper having a viscous fluid sealed in a gap and a spring element having an elastic body, and the viscous damper and the spring element are connected in series.
The viscous mass damper with a spring has a modulus of elasticity 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 axis of the viscous mass damper in the linear motion direction. The damper natural frequency ω corresponding to the apparent inertia mass m, which is the value obtained by dividing the reaction force acting in the linear motion direction by the relative acceleration when linearly moving at a predetermined relative acceleration, and the linear motion of the viscous mass damper And a damping coefficient c corresponding to a value obtained by dividing the reaction force acting in the linear motion direction by the relative velocity when the shaft is linearly moved at a constant relative velocity.
The damper natural frequency ωj (j = 1 to N) of the N viscous mass dampers with springs is different from each other.

The characteristics of the seismic isolation device or the vibration damping device are determined by combinations of different damper natural frequencies ωj (j = 1 to N) of the N spring mass viscous dampers.
Since the viscous mass damper with a spring is composed of an inertial mass, a viscous damper and a spring element, it has a natural frequency ω.
For example, a plurality of groups are constituted by N spring mass viscous dampers having different natural frequencies. N pieces of viscous mass dampers with springs belonging to a plurality of groups are arranged and attached between the support and the target structure or in the target structure.
Higher seismic isolation performance or damping performance can be exhibited as compared with a type in which each of the N damper mass dampers with springs has the same damper natural frequency ωj (j = 1 to N).
In the following, a seismic isolation device or damping device of a type in which each of the N spring mass viscous dampers has the same damper natural frequency ωj (j = 1 to N), damping coefficient, and inertial mass is “single”. The mold device "and the seismic isolation device or damping device according to the present invention are referred to as" multistage preparation type device ".
Unless otherwise specified, the sum of the inertia masses of the N spring mass viscous dampers provided in the single type device described below and the sum of the inertia masses of the N spring mass viscous dampers provided in the multistage adjustment type device Is equal to

FIG. 1 shows a model of a vibration system in which N spring mass viscous dampers are added to a target structure supported by a main frame on the basis of a support.
A model of the target structure supported by the main frame on the basis of the support is called a main system.
here,
u is a relative displacement in a specific direction of the main system.
Ms is an inertial mass applied to the relative displacement in a specific direction of the main system.
Ks is an elastic coefficient according to relative displacement in a specific direction of the main system.
Cs is an attenuation coefficient applied to the relative displacement in a specific direction of the main system.
ωs is a natural frequency applied to a relative displacement in a specific direction of the main system.
mj (j = 1 to N) is an apparent inertial mass with a viscous mass damper with a spring.
kbj (j = 1 to N) is an elastic coefficient of the viscous mass damper with a spring.
cj (j = 1 to N) is a damping coefficient of the viscous mass damper with a spring.
ωj (j = 1 to N) is the natural frequency of the viscous mass damper with a spring.
The natural frequency of a viscous mass damper with a spring is called a damper natural frequency.

The response magnification is used to evaluate the seismic isolation performance of the seismic isolation device or the damping performance of the vibration control device.
For example, the response magnification for evaluating the degree of vibration is a dynamic response magnification, a displacement response magnification, or an acceleration response magnification.
The dynamic response magnification is a ratio between the static displacement of the target structure due to the excitation force when the target structure is forcedly excited and the amplitude of the target structure that vibrates in response.
The displacement response magnification is a ratio between the displacement of the support when the support is forcibly excited and the displacement of the target structure that vibrates in response.
The acceleration response magnification 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.

An example of a viscous mass damper with a spring will be described with reference to the drawings.
FIG. 39 is a cross-sectional view showing an example of a viscous mass damper according to an embodiment of the present invention.
FIG. 40 is a cross-sectional view showing an example of a spring element according to the embodiment of the present invention.
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 “a system in which an inertia connecting element and a damper element are connected in parallel”.
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 inertia mass m 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 m.
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 an elastic body 210.
For example, 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 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 a “spring element”.
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.

FIG. 41 is a conceptual diagram showing an example of a mounting structure of a viscous mass damper with a spring according to the embodiment of the present invention.
A spring-equipped viscous mass damper in which a viscous mass damper and a spring element 200 are connected in series is attached between the support and the target structure or in the middle of the target structure.
The longitudinal direction of the linear motion axis of the viscous mass damper coincides with a specific direction generated by vibration of the target structure.

In the following, the seismic isolation device or the vibration damping device according to the embodiment of the present invention is set so that the damper natural frequencies ωj (j = 1 to N) of the N spring mass viscous dampers are different from each other. A description will be given according to various methods.
When it appears in the equation, the relationship between the attenuation constant h and the attenuation coefficient c is as follows.
c = 2hωm
An attenuation coefficient corresponding to the optimal attenuation constant is referred to as an optimal attenuation coefficient.

Initially, the seismic isolation apparatus or damping device which concerns on 1st embodiment of this invention is demonstrated.
FIG. 2 is a graph of the optimum tuning frequency ratio of the device according to the first embodiment of the present invention. FIG. 3 is a graph of the optimum attenuation constant of the device according to the first embodiment of the present invention.
The seismic isolation device or the vibration damping device according to the first embodiment of the present invention determines and sets specifications using the displacement response magnification as an evaluation criterion.

The N damper natural frequencies ωj (j = 1 to N) substantially correspond to the N optimum tuning frequencies, respectively.
Here, the N optimum tuning frequencies are assumed to be that each damper natural frequency ωj (j = 1 to N) of the N spring mass viscous dampers matches the N optimum tuning frequencies. The ratio p / ωs between the vibration frequency p and the natural frequency ωs of the vibration mode displaced in a specific direction of the system composed of the main frame and the target structure is set as the horizontal axis, and the response magnification of the target structure Is a vertical axis, and at least (N + 1) fixed points that are constant regardless of the value of the damping coefficient c of each of the N spring mass viscous dampers on the line indicating the response magnification. N damper natural frequencies ωj (j = 1 to N) whose values are substantially equal.

Further, the N attenuation coefficients c substantially match the N optimum attenuation coefficients.
Here, assuming that the N optimum attenuation coefficients are equal to the N optimum attenuation coefficients, the values at the (N + 1) fixed points are substantially substantially maximal. N attenuation coefficients c such that

Below, the case where the item of the two viscous mass dampers with a spring is determined is demonstrated to an example.
Unless otherwise specified, the apparent inertia mass mj (j = 1, 2) of each of the two spring-loaded viscous mass dampers is assumed to be equal.
The specifications are the natural frequency ω, the apparent inertia mass m, and the damping coefficient c.

上記の２つの式を満足する２個のバネ付き粘性マスダンパーの各々のダンパー固有振動数ω１、ω２が最適同調振動数である。 When p / ωs is the horizontal axis and the response magnification of the target structure is the vertical axis, the values of the respective damping coefficients c1 and c2 of the two spring-loaded viscous mass dampers on the line indicating the displacement response magnification. Regardless of the above, the conditional expression in which the values at at least three fixed points that are constant values are substantially equal is as follows.

The damper natural frequencies ω1 and ω2 of the two spring-loaded viscous mass dampers that satisfy the above two expressions are the optimum tuning frequencies.

上記の式を用いて、３個の定点での値が各々に実質的に略極大になる条件を求める。
例えば、上記の式より極大値を求め、求めた極大値が等しくなるｈ１、ｈ２の組み合わさせをパラメータスタディにより求める。
例えば、上記の式の微分式から定点が極大となる減衰定数ｈ１、ｈ２を求める。

上記の条件を満足する２個のバネ付き粘性マスダンパーの各々の減衰定数ｈ１、ｈ２が最適減衰定数である。 The displacement response magnification is obtained by the following equation.

Using the above equation, a condition is obtained in which the values at the three fixed points are each substantially substantially maximal.
For example, a maximum value is obtained from the above equation, and a combination of h1 and h2 at which the obtained maximum values are equal is obtained by a parameter study.
For example, the attenuation constants h1 and h2 at which the fixed points are maximized are obtained from the differential expression of the above expression.

The damping constants h1 and h2 of the two spring-loaded viscous mass dampers that satisfy the above conditions are the optimum damping constants.

Based on the drawings, the optimum tuning frequency and optimum damping constant of the two viscous mass dampers with springs will be described using the displacement response magnification as an evaluation criterion.
FIG. 2 is a graph of the optimum tuning frequency ratio of the device according to the first embodiment of the present invention. FIG. 3 is a graph of the optimum attenuation constant of the device according to the first embodiment of the present invention.
FIG. 2 shows the optimum tuning frequency ratio when the mass ratio is changed.
FIG. 3 shows the optimum attenuation constant when the mass ratio is changed.
The mass ratio is the ratio of the sum Σmj of the inertial mass of each of the N spring mass viscous dampers to the mass Ms of the main system.
The optimum tuning frequency ratio is the ratio between the optimum tuning frequency ωj and the natural frequency ωs of the main system.

The two curves in FIG. 2 represent the optimum tuning frequencies of the two spring-loaded viscous mass dampers, respectively. Once the mass ratio is determined, one of two optimal tuning frequencies can be selected.
Of the two optimum tuning frequencies, the optimum tuning frequency with the smaller optimum tuning frequency ratio is referred to as “soft”, and the optimum tuning frequency with the larger optimum tuning frequency ratio is referred to as “hard”. Call it.
The two curves in FIG. 3 represent the optimum damping constants of the two spring mass viscous dampers, respectively. Once the mass ratio is determined, one of two optimal damping constants can be selected.
Of the two optimum attenuation constants, the optimum attenuation constant having a smaller value is referred to as “softer”, and the optimum attenuation constant having a larger value is referred to as “harder”.
For both of the two spring-loaded viscous mass dampers, either the “harder” optimum tuning frequency ratio and optimum damping constant or the “softer” optimum tuning frequency ratio and optimum damping constant can be selected.
That is, one spring viscous mass damper selects the “harder” optimal tuning frequency ratio and optimal damping constant, and the other spring-loaded viscous mass damper selects the “softer” optimal tuning frequency ratio and optimal damping constant. If is selected, the conditional expression cannot be satisfied.

条件式を解析的に解くのは容易でないが、上記の近似式を用いることにより、簡便に採点同調振動数と最適減衰定数を選ぶことができる。 An approximate expression for obtaining the optimum tuning frequency ratio ν and the optimum damping constant h derived from the theoretical expression is as follows.

Although it is not easy to solve the conditional expression analytically, by using the above approximate expression, the scoring tuning frequency and the optimum damping constant can be easily selected.

The displacement response magnification when the two damper natural frequencies ωj (j = 1 to N) are set to values substantially corresponding to the two optimum tuning frequencies will be described with reference to the drawings.
FIG. 4 is a graph of the displacement response magnification of a single type device. FIG. 5 is a graph of displacement response magnification of the apparatus according to the first embodiment of the present invention. FIG. 6 is a graph of the maximum displacement response magnification of the apparatus according to the first embodiment of the present invention. FIG. 7 is an attenuation constant-maximum displacement response magnification graph 1 of the device according to the first embodiment of the present invention. FIG. 8 is an attenuation constant-maximum displacement response magnification graph 2 of the device according to the first embodiment of the present invention.

FIG. 4 shows the displacement response magnification of a single type device for comparison.
In the single-type device, two natural mass dampers with springs with the same specifications are used, and the natural vibration of the vibration mode that is displaced in a specific direction of the system composed of the excitation frequency p, the main frame, and the target structure When the ratio p / ωs to the number ωs is the horizontal axis and the displacement response magnification of the target structure is the vertical axis, the value of the damping coefficient c of the viscous mass damper with a spring on the line indicating the displacement response magnification is shown. Regardless of the above, the damper natural frequency is selected so that the values at at least two fixed points that are constant values are substantially equal, and the damping coefficient is selected so that the two fixed points have the maximum values.
The single-side device can select one of the “harder” and “softer” specifications, similar to the multistage adjustable device.
FIG. 5 shows that the damper natural frequency ωj of each of the two spring-loaded viscous mass dampers substantially matches the optimum tuning frequency corresponding to the two optimum tuning frequency ratios, and two damping coefficients are set to two. 3 shows a graph of the displacement response magnification of the system with the mass ratio as a parameter when the damping coefficient corresponding to the optimum damping constant is substantially matched to each other.
In FIG. 4 and FIG. 5, the response magnification when the optimum tuning frequency ratio and the optimum damping constant of the “softer” curve set with the symbols 1 to 5 or 1 to 7 is set is shown. , 1-5, or 1-7, the lower curve represents the response magnification when the optimum tuning frequency ratio and the optimum damping constant of “harder” are set.
In FIG. 5, the thin line indicates the displacement response magnification of the four-stage adjustable device.
The four-stage adjustment type device is a seismic isolation device or vibration control device that reduces the response magnification of the main system by using four spring-loaded viscous mass dampers having different specifications in order to suppress vibrations in a specific direction.

FIG. 6 shows the relationship between the mass ratio and the maximum value of the displacement response magnification.
Hereinafter, the maximum value of the displacement response magnification is referred to as the maximum displacement response magnification.
sψs is the maximum displacement response magnification of a single-type device in which the “softer” specifications are set.
Hψs is the maximum displacement response magnification of a single-type device in which the “harder” specifications are set.
sψd is the maximum displacement response magnification of the multistage adjustment type device in which the “softer” specifications are set.
Hψd is the maximum displacement response magnification of the multistage adjustment type apparatus in which the “harder” specifications are set.
7 and 8 show the relationship between the variation coefficient of the attenuation constant of the additional system and the change in the maximum value of the displacement response magnification.
FIG. 7 shows the response magnification of the softer single-type device and the two-stage adjustable device.
FIG. 8 shows the response magnification of the harder single-type device and the two-stage adjustable device.

The following can be understood from FIGS.
(1) There is a significant difference between the response magnification of the single-type device and the response magnification of the multistage adjustment type device.
(2) In particular, the response magnification of the multistage adjustment type device is significantly smaller around the natural frequency of the main system than the response magnification of the single type device.
(3) When the optimum tuning frequency ratio and optimum damping constant of the “softer” are set, the displacement response magnification of the multistage adjustment type device is more uniform than the displacement response magnification of the single type device at a mass ratio of 0.2 or less. Becomes smaller.
(4) When the optimal tuning frequency ratio and optimal damping constant of “harder” are set, the displacement response magnification of the multistage adjustment type device is uniformly smaller than the displacement response magnification of the single type device at all mass ratios. Become.
(5) A multistage preparation type device can set a smaller attenuation coefficient than a single type device to obtain an equivalent displacement response magnification.
(6) The multistage preparation type device has a wider natural frequency range than that of the single type device, which can obtain the same response magnification.
(7) A multistage preparation type apparatus can set a larger mass ratio than a single type apparatus. For example, the mass ratio in the single type is 0.25 or less, and the mass ratio in the multistage adjustment type apparatus is 0.352 or less.
(8) The seismic isolation effect and damping effect are not easily affected by fluctuations in the natural frequency of the main system. For example, the “softer” multistage adjustment type device is more advantageous than the single type device, particularly with a mass ratio of 0.2 or less and a fluctuation of the main system spring constant of 0.9 or more. The “harder” multistage adjustable device is more advantageous than the single device at all mass ratios.
In the above, the mass ratio generally includes an error of 0% to 10%, and the fluctuation of the spring constant of the main system includes an error of ± 5%.

Next, the seismic isolation device or the vibration damping device according to the second embodiment of the present invention will be described.
FIG. 9 is a graph of the optimum tuning frequency ratio of the device according to the second embodiment of the present invention. FIG. 10 is a graph of the optimum attenuation constant of the device according to the second embodiment of the present invention.
The seismic isolation device or the vibration damping device according to the second embodiment of the present invention sets specifications using the acceleration response magnification as an evaluation criterion.

The N damper natural frequencies ωj (j = 1 to N) substantially correspond to the N optimum tuning frequencies, respectively.
Here, the N optimum tuning frequencies are assumed to be that each damper natural frequency ωj (j = 1 to N) of the N spring mass viscous dampers matches the N optimum tuning frequencies. The ratio p / ωs between the vibration frequency p and the natural frequency ωs of the vibration mode displaced in a specific direction of the system composed of the main frame and the target structure is set as the horizontal axis, and the response magnification of the target structure Is a vertical axis, and at least (N + 1) fixed points that are constant regardless of the value of the damping coefficient c of each of the N spring mass viscous dampers on the line indicating the response magnification. N damper natural frequencies ωj (j = 1 to N) whose values are substantially equal.

Further, the N attenuation coefficients c substantially match the N optimum attenuation coefficients.
Here, assuming that the N optimum attenuation coefficients are equal to the N optimum attenuation coefficients, the values at the (N + 1) fixed points are substantially substantially maximal. N attenuation coefficients c such that

Below, the case where the item of the two viscous mass dampers with a spring is determined is demonstrated to an example.
Unless otherwise specified, the apparent inertia mass mj (j = 1, 2) of each of the two spring-loaded viscous mass dampers is assumed to be equal.
The specifications are natural frequency, apparent inertial mass, and damping coefficient.

上記の２つの式を満足する２個のバネ付き粘性マスダンパーの各々のダンパー固有振動数ω１、ω２が最適同調振動数である。 When p / ωs is the horizontal axis and the response magnification of the target structure is the vertical axis, the values of the respective damping coefficients c1 and c2 of the two spring-loaded viscous mass dampers on the line indicating the acceleration response magnification. Regardless of the above, the conditional expression in which the values at at least three fixed points that are constant values are substantially equal is as follows.

The damper natural frequencies ω1 and ω2 of the two spring-loaded viscous mass dampers that satisfy the above two expressions are the optimum tuning frequencies.

上記の式を用いて、３個の定点での値が各々に実質的に略極大になる条件を求める。
例えば、上記の式より極大値を求め、求めた極大値が等しくなるｈ１、ｈ２の組み合わせをパラメータスタディにより求める。
例えば、上記の式の微分式から定点が極大となる減衰定数ｈ１、ｈ２を求める。

上記の条件を満足する２個のバネ付き粘性マスダンパーの各々の減衰定数が最適減衰定数である。 The acceleration response magnification is obtained by the following equation.

Using the above equation, a condition is obtained in which the values at the three fixed points are each substantially substantially maximal.
For example, a maximum value is obtained from the above equation, and a combination of h1 and h2 at which the obtained maximum values are equal is obtained by a parameter study.
For example, the attenuation constants h1 and h2 at which the fixed points are maximized are obtained from the differential expression of the above expression.

The damping constant of each of the two spring mass dampers satisfying the above conditions is the optimum damping constant.

When the acceleration response magnification is used as an evaluation criterion, the optimum tuning frequency and optimum damping constant of the two viscous mass dampers with springs will be described with reference to the drawings.
FIG. 9 is a graph of the optimum tuning frequency ratio of the device according to the second embodiment of the present invention. FIG. 10 is a graph of the optimum attenuation constant of the device according to the second embodiment of the present invention.
FIG. 9 shows the optimum tuning frequency ratio when the mass ratio is changed.
FIG. 10 shows the optimum attenuation constant when the mass ratio is changed.
The mass ratio is the ratio of the sum Σmj of the inertial mass of each of the N spring mass viscous dampers to the mass Ms of the main system.
The optimum tuning frequency ratio is the ratio between the optimum tuning frequency ωj and the natural frequency ωs of the main system.

条件式を解析的に解くのは容易でないが、上記の近似式を用いることにより、簡便に最適同調振動数νと最適減衰定数ｈを選ぶことができる。 An approximate expression for obtaining the optimum tuning frequency ratio and the optimum damping constant derived from the theoretical formula is as follows.

Although it is not easy to solve the conditional expression analytically, the optimum tuning frequency ν and the optimum damping constant h can be easily selected by using the above approximate expression.

The acceleration response magnification when the two damper natural frequencies ωj (j = 1 to N) are substantially matched with the two optimum tuning frequencies, respectively, and the two damping coefficients are matched with the optimum damping coefficients, Based on the figure, it will be described in comparison with a single side.
FIG. 11 is a graph of the acceleration response magnification of the single-side device. FIG. 12 is a graph of the acceleration response magnification of the device according to the second embodiment of the present invention. FIG. 13 is a graph of the maximum acceleration response magnification of the device according to the second embodiment of the present invention. FIG. 14 is an attenuation constant-maximum acceleration response magnification graph of the device according to the second embodiment of the present invention.

FIG. 11 shows the acceleration response magnification of a single type device for comparison.
In the single-type device, two natural mass dampers with springs with the same specifications are used, and the natural vibration of the vibration mode that is displaced in a specific direction of the system composed of the excitation frequency p, the main frame, and the target structure When the ratio p / ωs to the number ωs is the horizontal axis and the acceleration response magnification of the target structure is the vertical axis, the value of the damping coefficient c of the viscous mass damper with a spring on the line indicating the acceleration response magnification. Regardless of the above, the damper natural frequency is selected so that the values at at least two fixed points that are constant values are substantially equal, and the damping coefficient is selected so that the two fixed points have the maximum values.
FIG. 12 shows the acceleration response magnification of the system when the damper natural frequency ωj and the damping constant of each of the two spring-loaded viscous mass dampers substantially match the optimum tuning frequency and the optimum damping constant, respectively. This is a graph using

FIG. 13 shows the relationship between the mass ratio and the maximum value of the acceleration response magnification.
Hereinafter, the maximum value of the acceleration response magnification is referred to as the maximum acceleration response magnification.
ψ ′s is the maximum acceleration response magnification of the single-type device.
ψ′d is the maximum acceleration response magnification of the multistage adjustment type device.
FIG. 14 shows the relationship between the variation coefficient of the attenuation constant of the additional system and the change in the maximum value of the acceleration response magnification.

The following can be understood from FIGS.
(1) There is a significant difference between the response magnification of the single-type device and the response magnification of the multistage adjustment type device.
(2) In particular, the response magnification of the multistage adjustment type device is significantly smaller around the natural frequency of the main system than the response magnification of the single type device.
(3) When the mass ratio is 0.1 or less, the displacement response magnification of the multistage adjustment type device is uniformly smaller than the acceleration response magnification of the single type device.
(4) A multistage preparation type device can set a smaller attenuation coefficient than a single type device to obtain an equivalent displacement response magnification.
(5) The multistage preparation type apparatus has a wider natural frequency range than that of the single type apparatus, which can obtain the same response magnification.
(6) A multistage preparation type apparatus can set a larger mass ratio than a single type apparatus. For example, the mass ratio in a single type is 0.499 or less, and the mass ratio in a multistage adjustment type apparatus is 0.992 or less.
(7) The seismic isolation effect and damping effect are not easily affected by fluctuations in the natural frequency of the main system. In particular, the mass ratio is 0.1 or less, and the variation of the spring constant of the main system is in the range of 0.98 to 1.02.
In the above, the mass ratio generally includes an error of 0% to 10%, and the fluctuation of the spring constant of the main system includes an error of ± 5%.

  Hereinafter, a method different from the method for determining the specifications of the viscous mass damper with spring described in the first or second embodiment will be described.

A seismic isolation device or vibration damping device according to a third embodiment of the present invention will be described.
In the seismic isolation device or the vibration damping device according to the third embodiment, the N damper natural frequencies ωj (j = 1 to N) are set to values that substantially match the N optimum tuning frequencies, respectively.
The N optimum tuning frequencies are assumed to be that each damper natural frequency ωj (j = 1 to N) of the N spring mass viscous dampers corresponds to the N optimum tuning frequencies, respectively. The ratio p / ωs between the vibration frequency p and the natural frequency ωs of the vibration mode displaced in a specific direction of the system composed of the main frame and the target structure is taken as the horizontal axis, and the response magnification of the target structure is taken as the vertical axis. Is the N damper natural frequencies at which the variation of each response magnification at the (N + 1) peak points having a maximum value on the line indicating the response magnification falls within a predetermined range. .
Further, the N attenuation coefficients cj (j = 1 to N) substantially coincide with the N optimum attenuation coefficients, respectively.
The N optimum damping coefficients indicate response magnifications when it is assumed that each damping coefficient cj (j = 1 to N) of the N spring mass viscous dampers matches the N optimum damping coefficients. N attenuation coefficients at which the average value of each response magnification at the N peak points having the maximum value on the line is substantially the minimum.

ここで、Ｐｍａｘは、応答倍率の極大値となる点である。
諸元の異なるＮ個のバネ付き粘性マスダンパーを備える場合、（Ｎ＋１）個の極大値が発生する。 The following is a functional expression G for calculating “variation of response magnification at each of (N + 1) peak points having a maximum value on a line indicating response magnification” and “maximum on a line indicating response magnification”. A functional expression H for calculating the “average value of response magnifications at N peak points having values” is shown.

Here, Pmax is a point at which the response magnification becomes a maximum value.
When N viscous mass dampers with springs having different specifications are provided, (N + 1) maximum values are generated.

A function G is selected by arbitrarily selecting a damper natural frequency ωj (j = 1 to N), a damping coefficient cj (j = 1 to N), and a mass ratio μ = Σmj / Ms of N viscous mass dampers with springs. Is determined to be less than a predetermined value and the function H is minimized.
Under a condition where the natural frequencies ωj (j = 1 to N) of the N viscous mass dampers with springs are different from each other, the function G tends to increase as the function H decreases. The required condition changes depending on the value setting.

Next, a seismic isolation device or a vibration damping device according to a fourth embodiment of the present invention will be described.
It is assumed that the N damper natural frequencies ωj (j = 1 to N) substantially coincide with the N optimum tuning frequencies, respectively.
The N optimum tuning frequencies are assumed to be that each damper natural frequency ωj (j = 1 to N) of the N spring mass viscous dampers corresponds to the N optimum tuning frequencies, respectively. The ratio p / ωs between the vibration frequency p and the natural frequency ωs of the vibration mode displaced in a specific direction of the system composed of the main frame and the target structure is taken as the horizontal axis, and the response magnification of the target structure is taken as the vertical axis. The N damper natural frequencies ωj (j for which the average value of each response magnification at the N peak points having the minimum value on the line indicating the response magnification is substantially minimized. = 1 to N).

ここで、Ｐｍｉｍは、応答倍率の極小値となる点である。
Ｎ個のバネ付き粘性マスダンパーを備える場合、Ｎ個の極小値が発生する。 A functional expression for calculating “the average value of each response magnification at N peak points having a minimum value on the line indicating the response magnification” is shown below.

Here, Pmim is a point at which the response magnification becomes a minimum value.
When N viscous mass dampers with springs are provided, N local minimum values are generated.

Next, a seismic isolation device or a vibration damping device according to a fifth embodiment of the present invention will be described.
The N damper natural frequencies ωj (j = 1 to N) substantially correspond to the N optimum tuning frequencies, respectively.
The N optimum tuning frequencies are assumed to be that each damper natural frequency ωj (j = 1 to N) of the N spring mass viscous dampers corresponds to the N optimum tuning frequencies, respectively. The ratio p / ωs between the vibration frequency p and the natural frequency ωs of the vibration mode displaced in a specific direction of the system composed of the main frame and the target structure is taken as the horizontal axis, and the response magnification of the target structure is taken as the vertical axis. , N damper natural frequencies ωj (j = 1) such that the average of the continuous response magnifications at the excitation frequency p having a predetermined width on the line indicating the response magnifications is substantially minimized. ~ N).

Next, an arrangement method and an attachment method of the N pieces of viscous mass dampers with springs will be described.
For example, a viscous mass damper set with a first spring having two or more N viscous mass dampers with a spring, and a viscous mass damper set with a second spring having two or more N viscous mass dampers with a spring With.
The N spring mass viscous dampers belonging to the first spring mass viscous damper set are referred to as N first spring mass viscous dampers.
The N spring mass viscous dampers belonging to the second spring mass viscous damper set are referred to as N second spring mass viscous dampers.
The damper natural frequency ωj (j = 1 to N) of N viscous mass dampers with first springs is different from each other, and the damper natural frequency ωj (j = 1 to N) of N second viscous mass dampers with springs Are different from each other.
The damping coefficients cj (j = 1 to N) of the N first viscous mass dampers with springs are different from each other, and the damping coefficients cj (j = 1 to N) of the N second viscous mass dampers with springs are different from each other.
The damper natural frequency ωj (j = 1 to N) of each of the N first spring-attached viscous mass dampers and the damper natural frequency ωj (j = 1 to N) of each of the N second spring-attached viscous mass dampers. ) Substantially coincide with each other, the damping coefficient cj (j = 1 to N) of each of the N first spring-attached viscous mass dampers (j = 1 to N) and the N second spring-attached viscosities. The damping coefficients cj (j = 1 to N) of the mass dampers (j = 1 to N) substantially coincide with each other.
N pieces of viscous mass dampers with first springs and N pieces of viscous mass dampers with second springs are point-symmetric with respect to each other with respect to the rigid center of the target structure, or the rigidity of symmetrical structures N pieces of viscous mass dampers with first springs and N pieces of viscous mass dampers with second springs are used as a support and target structure so that each pair is symmetrical with respect to a virtual line passing through the center. Or within each of the target structures.

For example, a plurality of sets of viscous mass dampers with springs are provided, each having two or more N viscous mass dampers with springs.
The damper natural frequency ωj (j = 1 to N) of N spring mass viscous dampers belonging to the same set of spring viscous mass damper sets is different, and N pieces belonging to the same set of spring viscous mass damper sets The damping coefficients cj (j = 1 to N) of the viscous mass dampers with springs are different from each other.
Each of the plurality of spring-attached viscous mass dampers obtained by selecting and combining one spring-attached viscous mass damper belonging to a different group from the whole of the N spring-attached viscous mass dampers belonging to the plurality of spring-attached viscous mass damper sets. The damper natural frequency ωj (j = 1 to N) is substantially equal to each other, and each of the N spring-loaded viscous mass dampers belonging to a plurality of spring-attached viscous mass damper sets has one spring belonging to a different set. The damping coefficients cj (j = 1 to N) of the plurality of spring-attached viscous mass dampers obtained by selecting and combining the viscous mass dampers substantially coincide with each other.
Each rotational moment acting around the rigid core of the target structure is canceled out by each group by the reaction force generated by each of N spring mass viscous dampers belonging to different sets of spring mass viscous dampers. In this way, each of N spring-loaded viscous mass dampers belonging to a plurality of sets of spring-attached viscous mass damper sets is attached between the support and the target structure or inside the target structure.

Below, the damper arrangement concerning the embodiment of the present invention is explained in full detail based on a figure.
First, the damper arrangement according to the first embodiment of the present invention will be described with reference to the drawings.
FIG. 15 is a conceptual diagram of a damper arrangement according to the first embodiment of the present invention.
The seismic isolation device or vibration damping device according to the first embodiment of the present invention includes four sets of spring-attached viscous mass damper sets each having three spring-attached viscous mass dampers.
The four sets of spring-loaded viscous mass damper sets each have three spring-loaded viscous mass dampers.
Four sets of viscous mass dampers with springs are called “viscous mass dampers with first springs”. They are referred to as “viscous mass damper set with second spring”, “viscous mass damper set with third spring”, and “viscous mass damper set with fourth spring”.
Each of the viscous mass dampers with springs belonging to the first to fourth spring-equipped viscous mass damper sets is referred to as a first to fourth viscous mass damper with a spring.

In the drawing, the three viscous mass dampers with springs are represented as Type-1, Type-2, and Type-3, respectively.
Viscous mass dampers with springs with different Type numbers have different specifications.
For example, spring-type viscous mass dampers with different Type numbers have different damper natural frequencies ω.
For example, spring-type viscous mass dampers having different Type numbers have mutually different elastic coefficients kb.
For example, spring-type viscous mass dampers with different Type numbers have different damping coefficients c.
For example, spring-type viscous mass dampers with different Type numbers have different inertial masses m.
The same spring type viscous mass damper with the same type number has the same specifications.
For example, a viscous mass damper with the same type number and a spring has the same damper natural vibration ω, the same elastic coefficient kb, the same damping coefficient c, and the same inertia mass m.
The support and the target structure are arranged so that the three viscous mass dampers with the first spring and the three viscous mass dampers with the second spring are point-symmetrical with respect to the rigid center of the target structure. Or between each floor of the target structure.
The support body and the target structure are arranged so that the three viscous mass dampers with the third spring and the three viscous mass dampers with the fourth spring are point-symmetric with respect to the rigid center of the target structure. Or between each floor of the target structure.

In this way, each rotational moment acting around the rigid core of the target structure by one reaction force generated by each of the N spring mass viscous dampers belonging to different sets of spring mass viscous dampers is one. Offset each pair.
Therefore, it can suppress that a torsion acts on a target structure by the reaction force which a viscous mass damper with a spring generates.

Next, the damper arrangement according to the second embodiment of the present invention will be described with reference to the drawings.
FIG. 16 is a plan view of a damper arrangement according to the second embodiment of the present invention.
The seismic isolation device or damping device according to the second embodiment of the present invention includes two sets of spring-attached viscous mass damper sets each having two spring-attached viscous mass dampers.
The target structure has a structure in which two tall target structures are connected by expansion.
The two sets of viscous mass dampers with springs each have two viscous mass dampers with springs.
Two sets of viscous mass dampers with springs are called “viscous mass dampers with first spring”. This is referred to as “second spring-attached viscous mass damper set”.
The first spring-attached viscous mass damper set is composed of two spring-attached viscous mass dampers.
The second spring-attached viscous mass damper set is composed of two spring-attached viscous mass dampers.

The spring-attached viscous mass damper belonging to the first spring-attached viscous mass damper set is referred to as a first spring-attached viscous mass damper.
A viscous mass damper with a spring belonging to the viscous mass damper set with a second spring is called a viscous mass damper with a second spring.

In the drawing, two first and second spring-loaded viscous mass dampers are represented as Type-1 and Type-2, respectively.
Viscous mass dampers with springs with different Type numbers have different specifications.
For example, spring-type viscous mass dampers with different Type numbers have different damper natural frequencies ω.
For example, spring-type viscous mass dampers having different Type numbers have mutually different elastic coefficients kb.
For example, spring-type viscous mass dampers with different Type numbers have different damping coefficients c.
For example, spring-type viscous mass dampers with different Type numbers have different inertial masses m.
The same spring type viscous mass damper with the same type number has the same specifications.
For example, a viscous mass damper with the same type number and a spring has the same damper natural vibration ω, the same elastic coefficient kb, the same damping coefficient c, and the same inertia mass m.
N so that the two viscous mass dampers with the first spring and the two viscous mass dampers with the second spring are symmetric with respect to each other with respect to the virtual line passing through the rigid center of the target structure. A plurality of viscous mass dampers with first springs and N second viscous mass dampers with springs are respectively attached between the support and the target structure or inside the target structure.
That is, between the support and the target structure, the viscous mass dampers with the same spring of the Type number are symmetrical with respect to each other with respect to a virtual line passing through the rigid center of the target structure for each pair. Or it is arranged between each floor of the object structure.

In this way, each rotational moment acting around the rigid core of the target structure by one reaction force generated by each of the N spring mass viscous dampers belonging to different sets of spring mass viscous dampers is one. Each pair will cancel each other.
Therefore, it can suppress that a torsion acts on a target structure by the reaction force which a viscous mass damper with a spring generates.

Initially, the damper arrangement concerning 3rd embodiment of this invention is demonstrated based on a figure.
FIG. 17 is a conceptual diagram of a damper arrangement according to the third embodiment of the present invention.
The seismic isolation device or damping device according to the third embodiment of the present invention includes two sets of spring-attached viscous mass damper sets each having two spring-attached viscous mass dampers.
The target structure has a ramen structure.
A viscous mass damper with a spring is arranged as an oblique member in the ramen structure.
Two sets of viscous mass dampers with springs are provided.
Two sets of viscous mass dampers with springs are called “viscous mass dampers with first spring”. This is referred to as “second spring-attached viscous mass damper set”.
The first spring-attached viscous mass damper set has two spring-attached viscous mass dampers.
The second spring-attached viscous mass damper set has two spring-attached viscous mass dampers.
The spring-loaded viscous mass dampers belonging to the first to second spring-loaded viscous mass damper sets are referred to as first to second spring-loaded viscous mass dampers, respectively.

In the drawing, two first and second spring-loaded viscous mass dampers are represented as Type-1 and Type-2, respectively.
Viscous mass dampers with springs with different Type numbers have different specifications.
For example, spring-type viscous mass dampers with different Type numbers have different damper natural frequencies ω.
For example, spring-type viscous mass dampers having different Type numbers have mutually different elastic coefficients kb.
For example, spring-type viscous mass dampers with different Type numbers have different damping coefficients c.
For example, spring-type viscous mass dampers with different Type numbers have different inertial masses m.
The same spring type viscous mass damper with the same type number has the same specifications.
For example, a viscous mass damper with the same type number and a spring has the same damper natural vibration ω, the same elastic coefficient kb, the same damping coefficient c, and the same inertia mass m.
The target structural band so that the two viscous mass dampers with the first spring and the two viscous mass dampers with the second spring are line symmetric with respect to each other with respect to an imaginary line passing through the rigid center of the target structure. Can be placed between floors.
That is, between the support and the target structure, the viscous mass dampers with the same spring of the Type number are symmetrical with respect to each other with respect to a virtual line passing through the rigid center of the target structure for each pair. Or it is arranged between each floor of the object structure.

In this way, each rotational moment acting around the rigid core of the target structure by one reaction force generated by each of the N spring mass viscous dampers belonging to different sets of spring mass viscous dampers is one. Offset each pair.
Therefore, it can suppress that a torsion acts on a target structure by the reaction force which a viscous mass damper with a spring generates.

Next, a damper mounting structure according to an embodiment of the present invention will be described.
First, the damper mounting structure according to the first embodiment of the present invention will be described with reference to the drawings.
FIG. 19 is a side view of the damper mounting structure according to the first embodiment of the present invention.
FIG. 19 shows a mounting structure when a viscous mass damper with a spring is arranged between the floors of the target structure.
Since the structure of the viscous mass damper with a spring is the same as that described above, the description thereof is omitted.
In FIG. 19A, the viscous damper and the spring element directly connected are arranged along the horizontal direction of the longitudinal direction of the linear motion shaft.
One end of the viscous mass damper with spring is fixed to the lower floor.
The other end of the spring-loaded viscous mass damper is fixed to a structural member extending downward from the upper floor.
FIG. 19B shows a structure in which a torque cancellation mechanism is provided between the viscous damper and the spring element. Other structures are the same as those shown in FIG.
When attached in this way, vibration accompanied by relative displacement with the horizontal direction of the upper and lower floors as a specific direction can be isolated or controlled.

Next, the damper attachment structure concerning 2nd embodiment of this invention is demonstrated based on a figure.
FIG. 20 is a side view of the damper mounting structure according to the second embodiment of the present invention.
FIG. 20 shows a mounting structure when the viscous mass damper with a spring is arranged between the floors of the target structure.
Since the structure of the viscous mass damper with a spring is the same as that described above, the description thereof is omitted.
In FIG. 19A, the viscous damper is connected in series to a plate-like spring structure suspended from above, and the linear motion shaft is disposed along the horizontal direction.
One end of the viscous mass damper is fixed to the lower floor.
The other end of the viscous mass damper is fixed to a plate-like spring element extending downward from the upper floor.
FIG. 19B shows a structure in which a torque cancellation mechanism is provided between the viscous damper and the spring element. Other structures are the same as those shown in FIG.
When attached in this way, vibration accompanied by relative displacement with the horizontal direction of the upper and lower floors as a specific direction can be isolated or controlled.

Next, a damper mounting structure according to a third embodiment of the present invention will be described with reference to the drawings.
FIG. 21 is a side view of the damper mounting structure according to the third embodiment of the present invention.
FIG. 21 shows a mounting structure when the viscous mass damper with spring is disposed obliquely between the floors of the target structure.
Since the structure of the viscous mass damper with a spring is the same as that described above, the description thereof is omitted.
In FIG. 21, what directly connected the viscous damper and the spring element is arranged along the oblique direction of the longitudinal direction of the linear motion shaft.
One end of the viscous mass damper with spring is fixed to the lower floor.
The other end of the spring-loaded viscous mass damper is fixed to the upper floor.
If attached in this way, vibration with relative displacement with the oblique direction as a specific direction can be isolated or controlled.

Next, a damper mounting structure according to a fourth embodiment of the present invention will be described with reference to the drawings.
FIG. 22 is a side view of a damper mounting structure according to the fourth embodiment of the present invention.
FIG. 22 shows a mounting structure when the viscous mass damper with a spring is vertically arranged between the floors of the target structure.
Since the structure of the viscous mass damper with a spring is the same as that described above, the description thereof is omitted.
In FIG. 22, the viscous damper and the spring element directly connected are arranged with the longitudinal direction of the linear motion shaft along the vertical direction.
One end of the viscous mass damper with spring is fixed to the lower floor.
The other end of the spring-loaded viscous mass damper is fixed to the upper floor.
If attached in this way, vibration with relative displacement with the vertical direction of the upper and lower floors in a specific direction can be isolated or controlled.

Next, a damper mounting structure according to a fifth embodiment of the present invention will be described based on the drawings.
FIG. 23 is a side view of the damper mounting structure according to the fifth embodiment of the present invention.
FIG. 23 shows a mounting structure when the viscous mass damper with a spring is horizontally disposed between the floors of the target structure.
The structure of the viscous mass damper with a spring is the same as that described above except that the linear motion shaft and the rotating body are provided at both ends of the frame.
In FIG. 23, the viscous damper is arranged with the longitudinal direction of the linear motion shaft along the vertical direction.
The central portion of the viscous damper is fixed to the elastic member descending from the upper floor.
Both ends of the spring-loaded viscous mass damper are fixed to the lower floor.
When attached in this way, vibration accompanied by relative displacement with the horizontal direction of the upper and lower floors as a specific direction can be isolated or controlled.

A springy viscous mass damper having a structure different from the structure described above will be described.
FIG. 25 is a side view of the damper mounting structure according to the sixth embodiment of the present invention.
The difference from the previously described viscous mass damper with spring will be described.
The rotating body has a disk shape, and the viscous fluid is sealed between the side surface of the disk and the frame.

Next, in the seismic isolation device or the vibration damping device according to the first embodiment, the seismic isolation performance or the vibration damping performance when the main system vibration characteristics are changed will be described with reference to the drawings.
FIG. 26 is a graph 1 showing a change in the maximum displacement response magnification of the device according to the first embodiment of the present invention.
FIG. 26 shows the maximum value of the displacement response magnification when the spring constant of the main system changes in the seismic isolation device or the vibration control device having the “softer” damper natural frequency that optimizes the displacement response magnification. Yes.
In the graph, the horizontal axis indicates the ratio between the spring constant of the main system and the spring constant of the main system when the optimum response magnification is obtained. The vertical axis represents the maximum value of the displacement response magnification.
For comparison, data for a single type device is also shown.

From FIG. 26, the following can be said.
(1) In the two-stage adjustment type device, the change in the maximum displacement response magnification tends to be less overall as compared with the single side device.
(2) In particular, the seismic isolation performance or damping performance of the two-stage adjustable device is more specific to the main system than the single-type device when the mass ratio is 0.2 or less and the spring constant fluctuation ratio is 0.9 or more Less susceptible to changes in frequency.
(3) In particular, the seismic isolation performance or damping performance of the two-stage adjustment type device is less susceptible to fluctuations in the damping coefficient when the mass ratio is 0.2 or less and the spring constant fluctuation ratio is 0.9 or more.
In the above, the mass ratio generally includes an error of 0% to 10%, and the fluctuation of the spring constant of the main system includes an error of ± 5%.

FIG. 27 is a graph 2 showing a change in the maximum displacement response magnification of the device according to the first embodiment of the present invention.
FIG. 27 shows the maximum value of the displacement response magnification when the spring constant of the main system is changed in the seismic isolation device or the vibration control device having the “harder” damper natural frequency that optimizes the displacement response magnification. Yes.
In the graph, the horizontal axis indicates the ratio between the spring constant of the main system and the spring constant of the main system when the optimum response magnification is obtained. The vertical axis represents the maximum value of the displacement response magnification.
For comparison, data for a single type device is also shown.

From FIG. 27, the following can be said.
(1) In the two-stage adjustment type device, the change in the maximum displacement response magnification tends to be less overall as compared with the single side device.
(2) In particular, the seismic isolation performance or damping performance of the two-stage adjustable device is less susceptible to changes in the natural frequency of the main system than the single-type device at all mass ratios.
(3) In particular, the seismic isolation performance or damping performance of the two-stage adjustable device is not easily affected by fluctuations in the damping coefficient at all mass ratios.

Next, in the seismic isolation device or damping device according to the second embodiment, the seismic isolation performance or damping performance when the main system vibration characteristics change will be described with reference to the drawings.
FIG. 28 is a graph 1 showing a change in the maximum acceleration response magnification of the device according to the second embodiment of the present invention.
FIG. 28 shows the maximum value of the acceleration response magnification when the natural frequency of the main system changes in the seismic isolation device or the vibration damping device having the damper natural frequency that optimizes the acceleration response magnification.
In the graph, the horizontal axis indicates the ratio between the spring constant of the main system and the spring constant of the main system when the optimum response magnification is obtained. The vertical axis represents the maximum value of the acceleration response magnification.
For comparison, data for a single type device is also shown.

The following can be said from the graph of FIG.
(1) In the two-stage adjustment type apparatus, the change in the maximum displacement response magnification tends to be less overall as compared with the single type apparatus.
(2) In particular, the seismic isolation performance or damping performance of the two-stage adjustment type device is greater than that of the single type device in the variation range where the mass ratio is 0.1 or less and the spring constant is 0.98 to 1.02. Less susceptible to changes in the natural frequency of the system.
(3) In particular, the seismic isolation performance or damping performance of the two-stage adjustable device is affected by fluctuations in the damping constant when the mass ratio is 0.1 or less and the spring constant is 0.98 to 1.02. Hateful.
In the above, the mass ratio generally includes an error of 0% to 10%, and the fluctuation of the spring constant of the main system includes an error of ± 5%.

Next, a seismic isolation device or a vibration damping device according to a sixth embodiment of the present invention will be described.
Of the N damper natural frequencies ωj (j = 1 to N), the lower damper natural frequency ωj is a value lower than the lower optimum tuning frequency of the N optimum tuning frequencies.
Alternatively, the lower damper natural frequency ωj of N damper natural frequencies ωj (j = 1 to N) is lower than the lower optimal tuning frequency of the N optimal tuning frequencies. Yes, of the N damper natural frequencies ωj (j = 1 to N), the higher damper natural frequency ωj substantially matches the higher one of the N optimum tuned frequencies.
Further, the lower damper natural frequency ωj among the N damper natural frequencies ωj (j = 1 to N) is lower than the lower optimum tuning frequency among the N optimum tuning frequencies. Yes, of the N damper natural frequencies ωj (j = 1 to N), the higher damper natural frequency ωj is slightly shifted from the higher optimal tuning frequency of the N optimal tuning frequencies. Value.
Alternatively, the lower damper natural frequency ωj of N damper natural frequencies ωj (j = 1 to N) is lower than the lower optimal tuning frequency of the N optimal tuning frequencies. Yes, of the N damper natural frequencies ωj (j = 1 to N), the higher damper natural frequency ωj is higher than the higher one of the N optimum tuned frequencies. is there.

Of the N damper natural frequencies ωj (j = 1 to N), the higher damper natural frequency ωj is higher than the higher one of the N optimum tuned frequencies.
Alternatively, the lower damper natural frequency ωj of N damper natural frequencies ωj (j = 1 to N) substantially matches the lower optimal tuning frequency of the N optimal tuning frequencies, Of the N damper natural frequencies ωj (j = 1 to N), the higher damper natural frequency ωj is higher than the higher one of the N optimum tuned frequencies.
Alternatively, the lower damper natural frequency ωj out of the N damper natural frequencies ωj (j = 1 to N) is slightly shifted from the lower optimal tuning frequency among the N optimal tuning frequencies. Of the N damper natural frequencies ωj (j = 1 to N), the higher damper natural frequency ωj is higher than the higher optimal tuning frequency of the N optimal tuning frequencies. Value.

“Higher” means “higher of the whole”.
“Lower” means “lower in the whole”.
For example, “higher” means “higher than average”.
For example, “lower” means “lower than average”.

  Here, the N optimum tuning frequencies are assumed to be that each damper natural frequency ωj (j = 1 to N) of the N spring mass viscous dampers matches the N optimum tuning frequencies. The ratio p / ωs between the vibration frequency p and the natural frequency ωs of the vibration mode displaced in a specific direction of the system composed of the main frame and the target structure is set as the horizontal axis, and the response magnification of the target structure Is a constant value regardless of the value of the N damping coefficients c, which is a value obtained by dividing the damping resistance force of the N damper elements by the relative speed on the line indicating the response magnification. It is a value of N damper natural frequencies ωj (j = 1 to N) such that values at (N + 1) fixed points are substantially equal.

Further, the N attenuation coefficients c substantially coincide with the N optimum attenuation coefficients.
Here, the optimal attenuation coefficient is such that the value at (N + 1) fixed points is substantially substantially maximum in each of the N attenuation coefficients c, assuming that the N attenuation coefficients c match the N optimal attenuation coefficients. N attenuation coefficients.

The characteristics of the seismic isolation device or the vibration damping device according to the sixth embodiment of the present invention will be described below based on calculation examples in a plurality of cases.
Hereinafter, a value obtained by subtracting the optimum natural frequency from the damper natural frequency and dividing the value by the optimum natural frequency is referred to as “shift amount”.
The fluctuation of the natural frequency of the main system will be described as the fluctuation of the spring constant of the main system. The same is true for the mass variation of the main system.

FIG. 29 is a graph showing a change in the maximum displacement response magnification of case 1 according to the sixth embodiment of the present invention.
In case 1, when the mass ratio is 0.1, of the two damper natural frequencies ωj (j = 1 to N), the lower damper natural frequency ωj is the optimal tuning frequency of the two The value is lower than the lower optimal tuning frequency, and the higher damper natural frequency ωj of the two damper natural frequencies ωj (j = 1 to N) is the value of the two optimal tuning frequencies. It is a value higher than the higher optimum tuning frequency.
The ratio of the shift amount toward the lower side and the shift amount toward the higher side is 1: 1.
From this result, the following can be understood.
(1) When it is assumed that the fluctuation of the spring constant of the main system changes in the range of 0.7 to 1.3. The maximum value of the response magnification decreases with the fluctuation of 0.7 and the fluctuation of 1.3.
A hard spring has the same effect of reducing the response magnification with the same shift amount.
(2) When the fluctuation of the spring constant of the main system is assumed to be in the range of 0.9 to 1.1. With the softer spring, the maximum value of the response magnification decreases up to a displacement of 3.5%. When it is 3.5% or more, the reduction effect becomes worse.
With the harder spring, the maximum value of the response magnification is reduced up to a shift amount of 1.5%, but when it is 1.5% or more, the reduction effect becomes worse.
From the above, it is determined that there is an appropriate shift amount.
Assuming the fluctuation range of the spring constant of the main system, an appropriate shift amount can be determined. The harder spring can be expected to have a greater reduction effect with a smaller shift amount than the softer spring.

FIG. 30 is a graph showing a change in the maximum displacement response magnification of case 2 according to the sixth embodiment of the present invention.
In case 2, when the mass ratio is 0.1, the lower damper natural frequency ωj of the two damper natural frequencies ωj (j = 1 to N) is The value is higher than the lower optimum tuning frequency, and the higher damper natural frequency ωj of the two damper natural frequencies ωj (j = 1 to N) is the higher of the two optimum tuning frequencies. Lower than the optimum tuning frequency of
The ratio of the shift amount toward the lower side and the shift amount toward the higher side is 1: 1.
From this result, the following can be understood.
(1) Under the condition of Case 2, no matter how the fluctuation of the spring constant of the main system is assumed, the response magnification increases as the shift amount of either the hard spring or the soft spring increases.

FIG. 31 is a graph showing changes in the maximum displacement response magnification of case 3 according to the sixth embodiment of the present invention.
In the case 3, when the mass ratio is 0.1, the lower damper natural frequency ωj of the two damper natural frequencies ωj (j = 1 to N) is The value is lower than the lower optimal tuning frequency, and the higher damper natural frequency ωj of the two damper natural frequencies ωj (j = 1 to N) is the value of the two optimal tuning frequencies. It is a value higher than the higher optimum tuning frequency.
The ratio of the shift amount toward the lower side and the shift amount toward the higher side is 2: 1.
From this result, the following can be understood.
(1) When the amount of the softer spring is doubled in the case 1, the maximum value of the response magnification decreases with a fluctuation of the spring constant of the main system of 0.7.
There is no change in the response magnification when the spring constant fluctuation of the main system is 1.3.

FIG. 32 is a graph showing changes in the maximum displacement response magnification of the case 4 according to the sixth embodiment of the present invention.
In the case 4, when the mass ratio is 0.1, the lower damper natural frequency ωj of the two damper natural frequencies ωj (j = 1 to N) is The value is lower than the lower optimal tuning frequency, and the higher damper natural frequency ωj of the two damper natural frequencies ωj (j = 1 to N) is the value of the two optimal tuning frequencies. It is a value higher than the higher optimum tuning frequency.
The ratio of the shift amount toward the lower side and the shift amount toward the higher side is 3: 1.
From this result, the following can be understood.
(1) When the amount of shift of the softer spring is 1.5 times that of Case 2, the maximum value of the response magnification with a fluctuation of the main system spring constant of 0.7 decreases. The response magnification near the fluctuation of the spring constant of the main system of 0.8 to 1.2 is larger than that of Case 2.
(2) When the shift amount is -15% and + 5%, the fluctuation of the spring constant of the main system is 1.0 and the maximum value is obtained.

FIG. 33 is a graph showing changes in the maximum displacement response magnification of case 5 according to the sixth embodiment of the present invention.
In the case 5, when the mass ratio is 0.1, the lower damper natural frequency ωj of the two damper natural frequencies ωj (j = 1 to N) is The value is lower than the lower optimal tuning frequency, and the higher damper natural frequency ωj of the two damper natural frequencies ωj (j = 1 to N) is the value of the two optimal tuning frequencies. It is a value higher than the higher optimum tuning frequency.
The ratio of the shift amount toward the lower side and the shift amount toward the higher side is 4: 1.
From this result, the following can be understood.
(1) The maximum value is shifted to a fluctuation of the main system spring constant of 1.0 or less.
(2) If the shift amount of the softer spring constant is 1.3 times that of Case 3, the maximum value of the response magnification becomes large when the shift amount of the main system spring constant is 0.7 and the shift amount is 16% or more.
(2) From this, it can be seen that there is an appropriate shift amount.

FIG. 34 is a graph showing changes in the maximum displacement response magnification of the case 6 according to the sixth embodiment of the present invention.
In the case 6, when the mass ratio is 0.2, the lower damper natural frequency ωj of the two damper natural frequencies ωj (j = 1 to N) is The value is lower than the lower optimal tuning frequency, and the higher damper natural frequency ωj of the two damper natural frequencies ωj (j = 1 to N) is the value of the two optimal tuning frequencies. It is a value higher than the higher optimum tuning frequency.
The ratio of the shift amount toward the lower side and the shift amount toward the higher side is 1: 1.
From this result, the following can be understood.
(1) In the case of a mass ratio of 0.2, there is an effect that the response magnification is reduced when the fluctuation of the spring constant of the main system is 0.7 (the side depending on the soft spring).
(2) When the fluctuation of the spring constant of the main system is 1.3 (on the side depending on the hard spring), the response magnification becomes larger than the response magnification corresponding to the optimal solution based on the fixed point theory when the shift amount is 5% or more, and the effect is reduced.

FIG. 35 is a graph showing a change in the maximum displacement response magnification of the case 7 according to the sixth embodiment of the present invention.
In the case 7, when the mass ratio is 0.2, the lower damper natural frequency ωj of the two damper natural frequencies ωj (j = 1 to N) is The value is lower than the lower optimal tuning frequency, and the higher damper natural frequency ωj of the two damper natural frequencies ωj (j = 1 to N) is the value of the two optimal tuning frequencies. It is a value higher than the higher optimum tuning frequency.
The ratio of the shift amount toward the lower side and the shift amount toward the higher side is 1: 1.
From this result, the following can be understood.
(1) When the mass ratio is 0.2, the effect of fluctuation of the main system spring constant of 0.7 (the side depending on the soft spring) is almost the same as that of the case 6.
(2) The response magnification is smaller than that of the case 6 even when the fluctuation of the spring constant of the main system is 1.3 (the side depending on the hard spring).
(3) If the mass ratio is greater than 0.1, the response magnification on the side depending on the hard spring can be reduced even if the shift amount is small.

FIG. 36 is a graph showing changes in the maximum displacement response magnification of the case 8 according to the sixth embodiment of the present invention.
In the case 9, when the mass ratio is 0.22, the lower damper natural frequency ωj of the two damper natural frequencies ωj (j = 1 to N) is The value is lower than the lower optimal tuning frequency, and the higher damper natural frequency ωj of the two damper natural frequencies ωj (j = 1 to N) is the value of the two optimal tuning frequencies. It almost coincides with the higher optimal tuning frequency.
The ratio of the shift amount toward the lower side and the shift amount toward the higher side is 1: 1.
From this result, the following can be understood.
(1) In the case of a mass ratio of 0.25, there is an effect that the response magnification is reduced when the spring constant of the main system is 0.7 (the side depending on the soft spring).
(2) When the fluctuation of the spring constant of the main system is 1.3 (on the side depending on the hard spring), the shift amount is 2% or more, and the response magnification becomes larger than the response magnification corresponding to the optimal solution according to the fixed point theory, and the effect is reduced.
(3) When the mass ratio is greater than 0.2, the response magnification of the variation 1.3 does not increase even with the same shift amount.

  From the above results, the lower damper natural frequency ωj among the N damper natural frequencies ωj (j = 1 to N) is more than the lower optimal tuning frequency among the N optimum tuning frequencies. The lower damper natural frequency ωj (j = 1 to N) is set to a lower value, and the higher damper natural frequency ωj is set to the higher optimum tuning frequency among the N optimum tuning frequencies. If it is set so as to be substantially coincident or slightly shifted, it is predicted that the fluctuation of the response magnification will be small even if the natural frequency of the main system fluctuates.

Next, a seismic isolation device or a vibration damping device according to a seventh embodiment of the present invention will be described with reference to the drawings.
FIG. 37 is a conceptual diagram showing a robust optimization method of the apparatus according to the seventh embodiment of the present invention. FIG. 38 is a graph showing changes in the maximum displacement response magnification of the device according to the seventh embodiment of the present invention.
The seismic isolation device or damping device according to the seventh embodiment is the same as the seismic isolation device or damping device according to the sixth embodiment, except that each of the N damper natural frequencies ωj (j = 1 to N). The damper natural frequency ωj substantially matches the N predetermined values.
Assuming that N damper natural frequencies ωj (j = 1 to N) correspond to the N predetermined values, the N predetermined values are equal to the minimum natural frequency ωmin and the maximum natural vibration. The maximum value Pmax on the line indicating the response magnification when taking a value between several ωmax is lower than the maximum value Pmax when the natural frequency ωs is the minimum natural frequency ωmin and the natural frequency ωs is the maximum N damper natural frequencies ωj that are lower than the maximum value Pmax at the natural frequency ωmax.
FIG. 38 shows an example of the displacement response magnification of the seismic isolation device or damping device according to the seventh embodiment.
In the figure, the displacement response magnification of the seismic isolation device or the vibration damping device according to the seventh embodiment is shown as an adjustment example. The broken line indicates the displacement response magnification of the single-type device. The solid line indicates the displacement response magnification of the seismic isolation device or the vibration damping device according to the first embodiment.
When N damper natural frequencies ωj are determined as described above, the variation of the displacement response magnification is small when the natural frequency ωs is within the range of the minimum natural frequency ωmin and the maximum natural frequency ωmax.
Therefore, even if the inertial mass or elastic coefficient of the main system changes and the natural frequency changes, the main system vibration can be effectively isolated and controlled.

Further, as described above, the seismic isolation device or the vibration damping device according to the present invention has the following effects due to its configuration.
A spring that is a system in which a viscous mass damper and a spring element are connected in series, which is a system in which an inertia connecting element and a damper element that convert relative displacement in a specific direction generated by vibration into a rotation amount of a rotating body are connected in parallel A plurality of viscous mass dampers with springs are prepared, and a plurality of viscous mass dampers with springs are respectively attached to the target structure, and the respective natural frequencies ωj (j = 1 to N) of the dampers having the plurality of viscous mass dampers with springs are mutually connected. Since they are made different, the N viscous mass dampers with springs having different damper natural frequencies disperse the vibration energy of the target structure in a wider frequency band and reduce the response.
A viscous mass with a spring which is a system in which a viscous mass damper composed of a linear motion shaft, a rotating body screwed into the linear motion shaft, and a viscous fluid enclosed in a gap between the rotational body and the frame and a spring element are connected in series. Prepare a plurality of dampers, attach a plurality of spring-equipped viscous mass dampers to the target structure, and have a plurality of damper-equipped mass dampers with different damper natural frequencies ωj (j = 1 to N) different from each other. Therefore, the N viscous mass dampers with springs having different damper natural frequencies disperse the vibration energy of the target structure in a wider frequency band and reduce the response.
Further, when p / ωs is the horizontal axis and the response magnification of the target structure is the vertical axis, the values of the respective damping coefficients c of the plurality of spring-attached viscous mass dampers on the line indicating the response magnification. Regardless, N damper natural frequencies ωj (j = 1 to N) are set so that the values at at least (N + 1) fixed points that are constant values are substantially equal. Therefore, (N + 1) fixed points are set. Therefore, the response magnification in the vicinity of the frequencies corresponding to (N + 1) fixed points can be equalized, and the peak response magnification can be lowered.
In addition, since N attenuation coefficients c are set so that the values at (N + 1) fixed points are substantially substantially maximal, the response magnification at (N + 1) fixed points has a maximum value. The overall response magnification is lowered from the peak response magnification.

Also, when p / ωs is the horizontal axis and the response magnification of the target structure is the vertical axis, the variation of each response magnification at (N + 1) peak points having a maximum value on a line indicating the response magnification. N damper natural frequencies ωj (j = 1 to N) are set so that is within a predetermined range, so that variation in response magnification at each of (N + 1) peak points having a maximum value is set. Falls within a predetermined range, and the response magnification near the peak point can be made uniform.
In addition, N attenuation coefficients cj (j = 1 to N) are set so that the average value of the response magnifications at the N peak points having the maximum values on the line indicating the response magnification is substantially minimized. Therefore, the response magnification in the vicinity of the peak can be lowered within a range where the variation of each response magnification at the (N + 1) peak points having the maximum value falls within a predetermined range.
Further, when p / ωs is taken as the horizontal axis and the response magnification of the target structure is taken as the vertical axis, the average value of each response magnification at N peak points having a minimum value on the line indicating the response magnification is Since N damper natural frequencies ωj (j = 1 to N) are set so as to be approximately the minimum, the average value of each response magnification at the N peak points having the minimum value is approximately the minimum. Thus, the response magnification near the N peak points can be lowered, and the overall response magnification can be lowered.
In addition, when p / ωs is the horizontal axis and the response magnification of the target structure is the vertical axis, the average of the continuous response magnifications at the excitation frequency p of a predetermined width on the line indicating the response magnification is substantially minimum. N damper natural frequencies ωj (j = 1 to N) are set so that the average of the continuous response magnifications at the excitation frequency p of a predetermined width becomes substantially minimum. The response magnification in the vicinity of the excitation frequency p of the width can be lowered.

Further, when p / ωs is the horizontal axis and the response magnification of the target structure is the vertical axis, N pieces which are values obtained by dividing the damping resistance force of the N damper elements by the relative speed on the line indicating the response magnification. N damper natural frequencies ωj (j = 1) rather than N optimum tuned frequencies at which the values at (N + 1) fixed points that are constant are substantially equal regardless of the value of the damping coefficient c. ˜N), the lower damper natural frequency ωj is set to a lower value, and the higher damper natural frequency ωj among the N damper natural frequencies ωj (j = 1 to N) is substantially matched. Since the value at the fixed point of the frequency wider than the (N + 1) fixed points is equal, the response magnification in the vicinity that is wider than the frequency corresponding to the (N + 1) fixed points is set. Can be made uniform, and the peak response magnification can be lowered.
Further, when p / ωs is the horizontal axis and the response magnification of the target structure is the vertical axis, N pieces which are values obtained by dividing the damping resistance force of the N damper elements by the relative speed on the line indicating the response magnification. N damper natural frequencies ωj (j = 1) rather than N optimum tuned frequencies at which the values at (N + 1) fixed points that are constant are substantially equal regardless of the value of the damping coefficient c. ˜N), the lower damper natural frequency ωj is set to a lower value, and the higher damper natural frequency ωj of the N damper natural frequencies ωj (j = 1 to N) is substantially matched. Since the value at the fixed point lower on the frequency side than (N + 1) fixed points is equal because the value is set to the value, the lower side is expanded to the lower side compared to the frequency corresponding to (N + 1) fixed points. The response magnification at You can. .
In addition, when p / ωs is the horizontal axis and the response magnification of the target structure is the vertical axis, N is a value obtained by dividing the damping resistance force of the N damper elements by the relative speed on the line indicating the response magnification. The N damper natural frequencies ωj (j = j = r) than the N optimum tuned frequencies at which the values at (N + 1) fixed points that are constant regardless of the values of the damping coefficients c are substantially equal. 1 to N), the higher damper natural frequency ωj is set to a higher value, and of the N damper natural frequencies ωj (j = 1 to N), the higher damper natural frequency ωj is substantially the same. Since the values at the fixed points higher on the frequency side than (N + 1) fixed points are equal, the lower side is expanded to the higher side compared to the frequencies corresponding to (N + 1) fixed points. Reduce the response magnification peak by equalizing the response magnification in the vicinity. be able to. .
In addition, since N attenuation coefficients c are set so that the values at (N + 1) fixed points are substantially substantially maximal, the response magnification at (N + 1) fixed points has a maximum value. The overall response magnification is lowered from the peak response magnification.

  Further, the maximum value Pmax on the line indicating the response magnification when the natural frequency ωs takes a value between the minimum natural frequency ωmin and the maximum natural frequency ωmax, and the natural frequency ωs is the minimum natural frequency ωmin. N damper natural frequencies ωj (j = 1 to N) are set so that the natural frequency ωs is lower than the maximum value Pmax when the natural frequency ωs is the maximum natural frequency ωmax. Therefore, when the natural frequency ωs of the vibration mode that is displaced in a specific direction of the system constituted by the main frame and the target structure is changed, the change in the response magnification is suppressed to a certain level.

In addition, each of the viscous mass dampers with a spring having a viscous mass damper with a spring having the same specifications, and each of the viscous mass dampers with a spring of the N second viscous mass dampers with a spring, Are arranged so as to be point symmetric with respect to each pair about the rigid body of the symmetric structure, so that each rotational moment around the rigid core cancels each other.
As a result, torsional motion induction can be suppressed in the system composed of the main frame and the target structure due to the reaction force of the viscous mass damper with spring, and the energy that induces torsional vibration can be isolated or controlled.
In addition, the rotational moment around the rigid core generated by the reaction force generated by the N spring mass viscous dampers belonging to each of the plurality of spring mass viscous dampers to which the spring mass viscous dampers whose specifications match each other belongs. A plurality of spring mass viscous dampers are attached between the support and the target structure or inside the target structure so as to cancel each other.
As a result, torsional motion induction can be suppressed in the system composed of the main frame and the target structure due to the reaction force of the viscous mass damper with spring, and the energy that induces torsional vibration can be isolated or controlled.

The present invention is not limited to the embodiments described above, and various modifications can be made without departing from the scope of the invention.
Although it demonstrated by the example provided with the N viscous mass dampers with a spring, you may provide other seismic isolation equipment and vibration control equipment in addition.

1 is a conceptual diagram of a seismic isolation device / vibration control device according to an embodiment of the present invention. It is a graph of the optimal tuning frequency ratio of the apparatus which concerns on 1st embodiment of this invention. It is a graph of the optimal attenuation constant of the apparatus which concerns on 1st embodiment of this invention. It is a graph of the displacement response magnification of a single type apparatus. It is a graph of the displacement response magnification of the apparatus which concerns on 1st embodiment of this invention. It is a graph of the maximum displacement response magnification of the apparatus which concerns on 1st embodiment of this invention. It is the attenuation constant-maximum displacement response magnification graph 1 of the apparatus which concerns on 1st embodiment of this invention. It is the attenuation constant-maximum displacement response magnification graph 2 of the apparatus which concerns on 1st embodiment of this invention. It is a graph of the optimal tuning frequency ratio of the apparatus which concerns on 2nd embodiment of this invention. It is a graph of the optimal damping constant of the apparatus which concerns on 2nd embodiment of this invention. It is a graph of the acceleration response magnification of the apparatus of the single side. It is a graph of the acceleration response magnification of the apparatus which concerns on 2nd embodiment of this invention. It is a graph of the maximum acceleration response magnification of the apparatus which concerns on 2nd embodiment of this invention. It is an attenuation constant-maximum acceleration response magnification graph of the apparatus concerning 2nd embodiment of this invention. It is a top view of damper arrangement concerning a first embodiment of the present invention. It is a top view of damper arrangement concerning a second embodiment of the present invention. It is a perspective view of damper arrangement concerning a third embodiment of the present invention. It is a conceptual diagram of the damper arrangement | positioning which concerns on 4th embodiment of this invention. . It is a side view of the damper attachment structure concerning a first embodiment of the present invention. It is a side view of the damper attachment structure concerning a second embodiment of the present invention. It is a side view of the damper attachment structure which concerns on 3rd embodiment of this invention. It is a side view of the damper mounting structure which concerns on 4th embodiment of this invention. It is a side view of the damper mounting structure which concerns on 5th embodiment of this invention. It is a top view of the damper attachment structure concerning a first embodiment of the present invention. It is a side view of the damper attachment structure concerning a 6th embodiment of the present invention. It is the graph 1 which shows the change of the maximum displacement response magnification of the apparatus which concerns on 1st embodiment of this invention. It is the graph 1 which shows the change of the maximum displacement response magnification of the apparatus which concerns on 1st embodiment of this invention. It is the graph 2 which shows the change of the maximum displacement response magnification of the apparatus which concerns on 2nd embodiment of this invention. It is a graph which shows the change of the maximum displacement response magnification of case 1 concerning a 6th embodiment of the present invention. It is a graph which shows the change of the maximum displacement response magnification of case 2 concerning a 6th embodiment of the present invention. It is a graph which shows the change of the maximum displacement response magnification of case 3 concerning a 6th embodiment of the present invention. It is a graph which shows the change of the maximum displacement response magnification of case 4 concerning a 6th embodiment of the present invention. It is a graph which shows the change of the maximum displacement response magnification of case 5 which concerns on 6th embodiment of this invention. It is a graph which shows the change of the maximum displacement response magnification of case 6 concerning a 6th embodiment of the present invention. It is a graph which shows the change of the maximum displacement response magnification of case 7 concerning a 6th embodiment of the present invention. It is a graph which shows the change of the maximum displacement response magnification of case 8 which concerns on 6th embodiment of this invention. It is a conceptual diagram which shows the robust optimization method of the apparatus which concerns on 7th embodiment of this invention. It is a graph which shows the change of the maximum displacement response magnification of the apparatus which concerns on 7th embodiment of this invention. It is sectional drawing which shows an example of the viscous mass damper which concerns on embodiment of this invention. It is sectional drawing which shows an example of the spring element which concerns on embodiment of this invention. It is a conceptual diagram which shows an example of the attachment structure of the viscous mass damper with a spring which concerns on embodiment of this invention.

Explanation of symbols

Ms Mass of main system Cs Damping coefficient of main system mj Apparent mass of viscous mass damper with spring cj Damping coefficient of viscous mass damper with spring kbj Elastic coefficient of viscous mass damper with spring μ Mass ratio ((Σmj) / Ms)
sψ 'Maximum displacement response magnification (soft)
hψ 'Maximum addition response magnification (hard)
ψ 'Maximum addition response magnification 5 Support 10 Target structure 11 Mounting portion 12 Mounting portion 13 Mounting portion 20 Main frame 30 Inertial connection element 40 Spring element 50 Damper element 100 Viscous mass damper 110 Linear guide 120 Linear motion shaft 130 Rotating body 131 Screw Nut 132 Rotating Cylinder 140 Frame 141 Thread 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

Claims (13)

A seismic isolation device or a vibration control device for damping the vibration of the target structure supported by the main frame on the basis of the support,
N spring mass viscous dampers that are 2 or more
Prepared,
An inertial connection element that converts a relative displacement in a specific direction generated by vibration of the viscous mass damper with a spring into a rotation amount of the rotating body, and an elastic reaction force that acts along the specific direction corresponding to the relative displacement in the specific direction. A system in which the inertia connecting element and the damper element are connected in parallel with a spring element that generates a damping force and a damper element that generates a damping resistance acting along a specific direction corresponding to a relative speed in a specific direction. A system in which a certain viscous mass damper and the spring element are connected in series,
The spring-equipped viscous mass damper has a damper natural frequency ω corresponding to an elastic coefficient kb of the spring element and an apparent inertia mass m with respect to a relative acceleration in a specific direction of the inertia connecting element, and the damping resistance force of the damper element. A damping coefficient c corresponding to the value divided by the relative velocity,
Or
The spring-attached 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 rotating body. A viscous mass damper having a viscous fluid sealed in a gap and a spring element having an elastic body, and the viscous mass damper and the spring element are connected in series,
An elastic coefficient kb which is a value obtained by dividing a reaction force generated when the spring-equipped viscous mass damper displaces the spring element by a relative distance in the linear motion direction, and the linear motion shaft of the viscous mass damper. To the apparent inertia mass m, which is a value obtained by dividing the reaction force generated by the inertial force of the rotating body 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. When the corresponding damper natural frequency ω and the linear motion shaft of the viscous mass damper are linearly moved at a constant relative speed, the reaction force generated by the damping resistance force of the viscous fluid acting in the linear motion direction is the relative force. A damping coefficient c corresponding to the value divided by the speed,
One of the
Here, the elastic coefficient kb, the apparent inertia mass m, and the damper natural frequency ω are in the following relationship:

The N viscous mass dampers with springs each having different damper natural frequencies ωj (j = 1 to N) are subject to relative displacement corresponding to the relative displacement in a specific direction of the target structure. Attached to the structure,
N damper natural frequencies ωj (j = 1 to N) substantially correspond to N optimum tuning frequencies, respectively.
Here, the N optimum tuning frequencies are expressed as a mass system having a structure in which the N viscous mass dampers with a spring and the main frame support the target structure in parallel on the basis of the support. The ratio p / ωs between the vibration frequency p obtained by numerical analysis of the mass system and the natural frequency ωs of one vibration mode displaced in a specific direction of the target structure is taken as the horizontal axis, In the graph with the response magnification as the vertical axis, each of the damper natural frequencies ωj (j = 1 to N) of the N viscous mass dampers with springs corresponds to the N optimal tuning frequencies. Assuming that, on the line indicating the relationship between the response magnification and the ratio p / ωs, a constant value is obtained regardless of the value of each damping coefficient c of the N viscous mass dampers with springs. The value of the response magnification at at least (N + 1) fixed points There are N number of the damper natural frequency ωj substantially equal ing,
The response magnification is a dynamic response magnification, which is a ratio between the static displacement of the target structure due to the excitation force when the target structure is forcedly vibrated and the amplitude of the target structure that vibrates in response. Vibration in response to the displacement response magnification, which is the ratio of the displacement of the support when it 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 One of the acceleration response magnifications, which is the ratio to the acceleration of the target object,
A seismic isolation device or a vibration control device. N attenuation coefficients cj (j = 1 to N) are values that approximately match the N optimal attenuation coefficients, respectively.
Here, the N optimum damping coefficients are expressed by a mass system having a structure in which the N viscous mass dampers with springs and the main frame support the target structure in parallel on the basis of the support. The ratio p / ωs between the vibration frequency p obtained by numerical analysis of the mass system and the natural frequency ωs of one vibration mode displaced in a specific direction of the target structure is taken as the horizontal axis, In the graph with the response magnification on the vertical axis, assuming that the N attenuation coefficients c match the N optimal attenuation coefficients, the response magnification values at the (N + 1) fixed points are respectively N attenuation coefficients cj that are substantially maximal.
The seismic isolation device or the vibration damping device according to claim 1. A seismic isolation device or a vibration control device for damping the vibration of the target structure supported by the main frame on the basis of the support,
N spring mass viscous dampers that are 2 or more
Prepared,
An inertial connection element that converts a relative displacement in a specific direction generated by vibration of the viscous mass damper with a spring into a rotation amount of the rotating body, and an elastic reaction force that acts along the specific direction corresponding to the relative displacement in the specific direction. A system in which the inertia connecting element and the damper element are connected in parallel with a spring element that generates a damping force and a damper element that generates a damping resistance acting along a specific direction corresponding to a relative speed in a specific direction. A system in which a certain viscous mass damper and the spring element are connected in series,
The spring-equipped viscous mass damper has a damper natural frequency ω corresponding to an elastic coefficient kb of the spring element and an apparent inertia mass m with respect to a relative acceleration in a specific direction of the inertia connecting element, and the damping resistance force of the damper element. A damping coefficient c corresponding to the value divided by the relative velocity,
Or
The spring-attached 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 rotating body. A viscous mass damper having a viscous fluid sealed in a gap and a spring element having an elastic body, and the viscous mass damper and the spring element are connected in series,
An elastic coefficient kb which is a value obtained by dividing a reaction force generated when the spring-equipped viscous mass damper displaces the spring element by a relative distance in the linear motion direction, and the linear motion shaft of the viscous mass damper. To the apparent inertia mass m, which is a value obtained by dividing the reaction force generated by the inertial force of the rotating body 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. When the corresponding damper natural frequency ω and the linear motion shaft of the viscous mass damper are linearly moved at a constant relative speed, the reaction force generated by the damping resistance force of the viscous fluid acting in the linear motion direction is the relative force. A damping coefficient c corresponding to the value divided by the speed,
One of the
Here, the elastic coefficient kb, the apparent inertia mass m, and the damper natural frequency ω are in the following relationship:

The N viscous mass dampers with springs each having different damper natural frequencies ωj (j = 1 to N) are subject to relative displacement corresponding to the relative displacement in a specific direction of the target structure. Attached to the structure,
N damper natural frequencies ωj (j = 1 to N) substantially correspond to N optimum tuning frequencies, respectively.
Here, the N optimum tuning frequencies are expressed as a mass system having a structure in which the N viscous mass dampers with a spring and the main frame support the target structure in parallel on the basis of the support. The ratio p / ωs between the vibration frequency p obtained by numerical analysis of the mass system and the natural frequency ωs of one vibration mode displaced in a specific direction of the target structure is taken as the horizontal axis, In the graph with the response magnification as the vertical axis, each of the damper natural frequencies ωj (j = 1 to N) of the N viscous mass dampers with springs corresponds to the N optimal tuning frequencies. when assuming, variations in response factor of each at (N + 1) pieces of peak point having the maximum value on the line indicating the relationship between the response magnification and the ratio p / .omega.s is that Osama within a predetermined range N The damper natural frequency ωj ,
The response magnification is a dynamic response magnification, which is a ratio between the static displacement of the target structure due to the excitation force when the target structure is forcedly vibrated and the amplitude of the target structure that vibrates in response. Vibration in response to the displacement response magnification, which is the ratio of the displacement of the support when it 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 One of the acceleration response magnifications, which is the ratio to the acceleration of the target object,
A seismic isolation device or a vibration control device. N attenuation coefficients cj (j = 1 to N) approximately match N optimal attenuation coefficients,
Here, the N optimum damping coefficients are expressed by a mass system having a structure in which the N viscous mass dampers with springs and the main frame support the target structure in parallel on the basis of the support. The ratio p / ωs between the vibration frequency p obtained by numerical analysis of the mass system and the natural frequency ωs of one vibration mode displaced in a specific direction of the target structure is taken as the horizontal axis, In the graph with the response magnification as the vertical axis, when it is assumed that the respective damping coefficients cj (j = 1 to N) of the N spring mass dampers with springs correspond to the N optimum damping coefficients, respectively. Are the N attenuation coefficients cj at which the average value of the response magnifications at the N peak points having the maximum value on the line indicating the relationship between the response magnification and the ratio p / ωs is substantially minimum. ,
The seismic isolation device or the vibration damping device according to claim 3. A seismic isolation device or a vibration control device for damping the vibration of the target structure supported by the main frame on the basis of the support,
N spring mass viscous dampers that are 2 or more
Prepared,
An inertial connection element that converts a relative displacement in a specific direction generated by vibration of the viscous mass damper with a spring into a rotation amount of the rotating body, and an elastic reaction force that acts along the specific direction corresponding to the relative displacement in the specific direction. A system in which the inertia connecting element and the damper element are connected in parallel with a spring element that generates a damping force and a damper element that generates a damping resistance acting along a specific direction corresponding to a relative speed in a specific direction. A system in which a certain viscous mass damper and the spring element are connected in series,
The spring-equipped viscous mass damper has a damper natural frequency ω corresponding to an elastic coefficient kb of the spring element and an apparent inertia mass m with respect to a relative acceleration in a specific direction of the inertia connecting element, and the damping resistance force of the damper element. A damping coefficient c corresponding to the value divided by the relative velocity,
Or
The spring-attached 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 rotating body. A viscous mass damper having a viscous fluid sealed in a gap and a spring element having an elastic body, and the viscous mass damper and the spring element are connected in series,
An elastic coefficient kb which is a value obtained by dividing a reaction force generated when the spring-equipped viscous mass damper displaces the spring element by a relative distance in the linear motion direction, and the linear motion shaft of the viscous mass damper. To the apparent inertia mass m, which is a value obtained by dividing the reaction force generated by the inertial force of the rotating body 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. When the corresponding damper natural frequency ω and the linear motion shaft of the viscous mass damper are linearly moved at a constant relative speed, the reaction force generated by the damping resistance force of the viscous fluid acting in the linear motion direction is the relative force. A damping coefficient c corresponding to the value divided by the speed,
One of the
Here, the elastic coefficient kb, the apparent inertia mass m, and the damper natural frequency ω are in the following relationship:

The N viscous mass dampers with springs each having different damper natural frequencies ωj (j = 1 to N) are subject to relative displacement corresponding to the relative displacement in a specific direction of the target structure. Attached to the structure,
N damper natural frequencies ωj (j = 1 to N) substantially correspond to N optimum tuning frequencies, respectively.
Here, the N optimum tuning frequencies are expressed as a mass system having a structure in which the N viscous mass dampers with a spring and the main frame support the target structure in parallel on the basis of the support. The ratio p / ωs between the vibration frequency p obtained by numerical analysis of the mass system and the natural frequency ωs of one vibration mode displaced in a specific direction of the target structure is taken as the horizontal axis, In the graph with the response magnification as the vertical axis, each of the damper natural frequencies ωj (j = 1 to N) of the N viscous mass dampers with springs corresponds to the N optimal tuning frequencies. when assuming, the response magnification and the ratio p / .omega.s and the average value of each of the response ratio in the N peak points having a very small value on the line indicating the relationship of N substantially minimum and ing of Damper natural frequency ωj ,
The response magnification is a dynamic response magnification, which is a ratio between the static displacement of the target structure due to the excitation force when the target structure is forcedly vibrated and the amplitude of the target structure that vibrates in response. Vibration in response to the displacement response magnification, which is the ratio of the displacement of the support when it 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 One of the acceleration response magnifications, which is the ratio to the acceleration of the target object,
A seismic isolation device or a vibration control device. A seismic isolation device or a vibration control device for damping the vibration of the target structure supported by the main frame on the basis of the support,
N spring mass viscous dampers that are 2 or more
Prepared,
An inertial connection element that converts a relative displacement in a specific direction generated by vibration of the viscous mass damper with a spring into a rotation amount of the rotating body, and an elastic reaction force that acts along the specific direction corresponding to the relative displacement in the specific direction. A system in which the inertia connecting element and the damper element are connected in parallel with a spring element that generates a damping force and a damper element that generates a damping resistance acting along a specific direction corresponding to a relative speed in a specific direction. A system in which a certain viscous mass damper and the spring element are connected in series,
The spring-equipped viscous mass damper has a damper natural frequency ω corresponding to an elastic coefficient kb of the spring element and an apparent inertia mass m with respect to a relative acceleration in a specific direction of the inertia connecting element, and the damping resistance force of the damper element. A damping coefficient c corresponding to the value divided by the relative velocity,
Or
The spring-attached 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 rotating body. A viscous mass damper having a viscous fluid sealed in a gap and a spring element having an elastic body, and the viscous mass damper and the spring element are connected in series,
An elastic coefficient kb which is a value obtained by dividing a reaction force generated when the spring-equipped viscous mass damper displaces the spring element by a relative distance in the linear motion direction, and the linear motion shaft of the viscous mass damper. To the apparent inertia mass m, which is a value obtained by dividing the reaction force generated by the inertial force of the rotating body 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. When the corresponding damper natural frequency ω and the linear motion shaft of the viscous mass damper are linearly moved at a constant relative speed, the reaction force generated by the damping resistance force of the viscous fluid acting in the linear motion direction is the relative force. A damping coefficient c corresponding to the value divided by the speed,
One of the
Here, the elastic coefficient kb, the apparent inertia mass m, and the damper natural frequency ω are in the following relationship:

The N viscous mass dampers with springs each having different damper natural frequencies ωj (j = 1 to N) are subject to relative displacement corresponding to the relative displacement in a specific direction of the target structure. Attached to the structure,
N damper natural frequencies ωj (j = 1 to N) substantially correspond to N optimum tuning frequencies, respectively.
Here, the N optimum tuning frequencies are expressed as a mass system having a structure in which the N viscous mass dampers with a spring and the main frame support the target structure in parallel on the basis of the support. The ratio p / ωs between the vibration frequency p obtained by numerical analysis of the mass system and the natural frequency ωs of one vibration mode displaced in a specific direction of the target structure is taken as the horizontal axis, In the graph with the response magnification as the vertical axis, each of the damper natural frequencies ωj (j = 1 to N) of the N viscous mass dampers with springs corresponds to the N optimal tuning frequencies. when assuming, the response magnification and the ratio p / relationship predetermined vibration the damper natural frequency average of N substantially minimum and ing the response magnification at a frequency p of a width on the line indicating the between ωs A number ωj ,
The response magnification is a dynamic response magnification, which is a ratio between the static displacement of the target structure due to the excitation force when the target structure is forcedly vibrated and the amplitude of the target structure that vibrates in response. Vibration in response to the displacement response magnification, which is the ratio of the displacement of the support when it 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 One of the acceleration response magnifications, which is the ratio to the acceleration of the target object,
A seismic isolation device or a vibration control device. A seismic isolation device or a vibration control device for damping the vibration of the target structure supported by the main frame on the basis of the support,
N spring mass viscous dampers that are 2 or more
Prepared,
An inertial connection element that converts a relative displacement in a specific direction generated by vibration of the viscous mass damper with a spring into a rotation amount of the rotating body, and an elastic reaction force that acts along the specific direction corresponding to the relative displacement in the specific direction. A system in which the inertia connecting element and the damper element are connected in parallel with a spring element that generates a damping force and a damper element that generates a damping resistance acting along a specific direction corresponding to a relative speed in a specific direction. A system in which a certain viscous mass damper and the spring element are connected in series,
The spring-equipped viscous mass damper has a damper natural frequency ω corresponding to an elastic coefficient kb of the spring element and an apparent inertia mass m with respect to a relative acceleration in a specific direction of the inertia connecting element, and the damping resistance force of the damper element. A damping coefficient c corresponding to the value divided by the relative velocity,
Or
The spring-attached 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 rotating body. A viscous mass damper having a viscous fluid sealed in a gap and a spring element having an elastic body, and the viscous mass damper and the spring element are connected in series,
An elastic coefficient kb which is a value obtained by dividing a reaction force generated when the spring-equipped viscous mass damper displaces the spring element by a relative distance in the linear motion direction, and the linear motion shaft of the viscous mass damper. To the apparent inertia mass m, which is a value obtained by dividing the reaction force generated by the inertial force of the rotating body 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. When the corresponding damper natural frequency ω and the linear motion shaft of the viscous mass damper are linearly moved at a constant relative speed, the reaction force generated by the damping resistance force of the viscous fluid acting in the linear motion direction is the relative force. A damping coefficient c corresponding to the value divided by the speed,
One of the
Here, the elastic coefficient kb, the apparent inertia mass m, and the damper natural frequency ω are in the following relationship:

The N viscous mass dampers with springs each having different damper natural frequencies ωj (j = 1 to N) are subject to relative displacement corresponding to the relative displacement in a specific direction of the target structure. Attached to the structure,
Of the N damper natural frequencies ωj (j = 1 to N), the damper natural frequency ωj lower than the average is lower than the average optimum tuning frequency of the N optimum tuning frequencies. Even lower values,
Of the N damper natural frequencies ωj (j = 1 to N), the damper natural frequency ωj that is higher than the average is set to the optimum tuning frequency that is higher than the average of the N optimum tuning frequencies. Nearly coincident or slightly off,
Here, the N optimum tuning frequencies are expressed as a mass system having a structure in which the N viscous mass dampers with a spring and the main frame support the target structure in parallel on the basis of the support. The ratio p / ωs between the vibration frequency p obtained by numerical analysis of the mass system and the natural frequency ωs of one vibration mode displaced in a specific direction of the target structure is taken as the horizontal axis, In the graph with the response magnification as the vertical axis, each of the damper natural frequencies ωj (j = 1 to N) of the N viscous mass dampers with springs corresponds to the N optimal tuning frequencies. Assuming that N damping coefficients c are values obtained by dividing the damping resistance force of the N damper elements by the relative speed on a line indicating the relationship between the response magnification and the ratio p / ωs. (N + 1) fixed points that are constant regardless of the value of An N-number of the damper natural frequency ωj value of the response magnification is substantially equal ing in,
The response magnification is a dynamic response magnification, which is a ratio between the static displacement of the target structure due to the excitation force when the target structure is forcedly vibrated and the amplitude of the target structure that vibrates in response. Vibration in response to the displacement response magnification, which is the ratio of the displacement of the support when it 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 One of the acceleration response magnifications, which is the ratio to the acceleration of the target object,
A seismic isolation device or a vibration control device. A seismic isolation device or a vibration control device for damping the vibration of the target structure supported by the main frame on the basis of the support,
N spring mass viscous dampers that are 2 or more
Prepared,
An inertial connection element that converts a relative displacement in a specific direction generated by vibration of the viscous mass damper with a spring into a rotation amount of the rotating body, and an elastic reaction force that acts along the specific direction corresponding to the relative displacement in the specific direction. A system in which the inertia connecting element and the damper element are connected in parallel with a spring element that generates a damping force and a damper element that generates a damping resistance acting along a specific direction corresponding to a relative speed in a specific direction. A system in which a certain viscous mass damper and the spring element are connected in series,
The spring-equipped viscous mass damper has a damper natural frequency ω corresponding to an elastic coefficient kb of the spring element and an apparent inertia mass m with respect to a relative acceleration in a specific direction of the inertia connecting element, and the damping resistance force of the damper element. A damping coefficient c corresponding to the value divided by the relative velocity,
Or
The spring-attached 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 rotating body. A viscous mass damper having a viscous fluid sealed in a gap and a spring element having an elastic body, and the viscous mass damper and the spring element are connected in series,
An elastic coefficient kb which is a value obtained by dividing a reaction force generated when the spring-equipped viscous mass damper displaces the spring element by a relative distance in the linear motion direction, and the linear motion shaft of the viscous mass damper. To the apparent inertia mass m, which is a value obtained by dividing the reaction force generated by the inertial force of the rotating body 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. When the corresponding damper natural frequency ω and the linear motion shaft of the viscous mass damper are linearly moved at a constant relative speed, the reaction force generated by the damping resistance force of the viscous fluid acting in the linear motion direction is the relative force. A damping coefficient c corresponding to the value divided by the speed,
One of the
Here, the elastic coefficient kb, the apparent inertia mass m, and the damper natural frequency ω are in the following relationship:

The N viscous mass dampers with springs each having different damper natural frequencies ωj (j = 1 to N) are subject to relative displacement corresponding to the relative displacement in a specific direction of the target structure. Attached to the structure,
Of the N damper natural frequencies ωj (j = 1 to N), the damper natural frequency ωj lower than the average is lower than the average optimum tuning frequency of the N optimum tuning frequencies. Even lower values,
Here, the N optimum tuning frequencies are expressed as a mass system having a structure in which the N viscous mass dampers with a spring and the main frame support the target structure in parallel on the basis of the support. The ratio p / ωs between the vibration frequency p obtained by numerical analysis of the mass system and the natural frequency ωs of one vibration mode displaced in a specific direction of the target structure is taken as the horizontal axis, In the graph with the response magnification as the vertical axis, each of the damper natural frequencies ωj (j = 1 to N) of the N viscous mass dampers with springs corresponds to the N optimal tuning frequencies. Assuming that N damping coefficients c are values obtained by dividing the damping resistance force of the N damper elements by the relative speed on a line indicating the relationship between the response magnification and the ratio p / ωs. (N + 1) fixed points that are constant regardless of the value of An N-number of the damper natural frequency ωj value of the response magnification is substantially equal ing in,
The response magnification is a dynamic response magnification, which is a ratio between the static displacement of the target structure due to the excitation force when the target structure is forcedly vibrated and the amplitude of the target structure that vibrates in response. Vibration in response to the displacement response magnification, which is the ratio of the displacement of the support when it 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 One of the acceleration response magnifications, which is the ratio to the acceleration of the target object,
A seismic isolation device or a vibration control device. A seismic isolation device or a vibration control device for damping the vibration of the target structure supported by the main frame on the basis of the support,
N spring mass viscous dampers that are 2 or more
Prepared,
An inertial connection element that converts a relative displacement in a specific direction generated by vibration of the viscous mass damper with a spring into a rotation amount of the rotating body, and an elastic reaction force that acts along the specific direction corresponding to the relative displacement in the specific direction. A system in which the inertia connecting element and the damper element are connected in parallel with a spring element that generates a damping force and a damper element that generates a damping resistance acting along a specific direction corresponding to a relative speed in a specific direction. A system in which a certain viscous mass damper and the spring element are connected in series,
The spring-equipped viscous mass damper has a damper natural frequency ω corresponding to an elastic coefficient kb of the spring element and an apparent inertia mass m with respect to a relative acceleration in a specific direction of the inertia connecting element, and the damping resistance force of the damper element. A damping coefficient c corresponding to the value divided by the relative velocity,
Or
The spring-attached 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 rotating body. A viscous mass damper having a viscous fluid sealed in a gap and a spring element having an elastic body, and the viscous mass damper and the spring element are connected in series,
An elastic coefficient kb which is a value obtained by dividing a reaction force generated when the spring-equipped viscous mass damper displaces the spring element by a relative distance in the linear motion direction, and the linear motion shaft of the viscous mass damper. To the apparent inertia mass m, which is a value obtained by dividing the reaction force generated by the inertial force of the rotating body 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. When the corresponding damper natural frequency ω and the linear motion shaft of the viscous mass damper are linearly moved at a constant relative speed, the reaction force generated by the damping resistance force of the viscous fluid acting in the linear motion direction is the relative force. A damping coefficient c corresponding to the value divided by the speed,
One of the
Here, the elastic coefficient kb, the apparent inertia mass m, and the damper natural frequency ω are in the following relationship:

The N viscous mass dampers with springs each having different damper natural frequencies ωj (j = 1 to N) are subject to relative displacement corresponding to the relative displacement in a specific direction of the target structure. Attached to the structure,
Of the N damper natural frequencies ωj (j = 1 to N), the higher of the damper natural frequencies ωj than the average of the N optimum tuned frequencies of the optimal tuned vibrations Higher than the number,
Here, the N optimum tuning frequencies are expressed as a mass system having a structure in which the N viscous mass dampers with a spring and the main frame support the target structure in parallel on the basis of the support. The ratio p / ωs between the vibration frequency p obtained by numerical analysis of the mass system and the natural frequency ωs of one vibration mode displaced in a specific direction of the target structure is taken as the horizontal axis, In the graph with the response magnification as the vertical axis, each of the damper natural frequencies ωj (j = 1 to N) of the N viscous mass dampers with springs corresponds to the N optimal tuning frequencies. Assuming that N damping coefficients c are values obtained by dividing the damping resistance force of the N damper elements by the relative speed on a line indicating the relationship between the response magnification and the ratio p / ωs . (N + 1) fixed points that are constant regardless of the value Wherein a damper natural frequency ωj of the N values of the response magnification is substantially equal ing,
The response magnification is a dynamic response magnification, which is a ratio between the static displacement of the target structure due to the excitation force when the target structure is forcedly vibrated and the amplitude of the target structure that vibrates in response. Vibration in response to the displacement response magnification, which is the ratio of the displacement of the support when it 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 One of the acceleration response magnifications, which is the ratio to the acceleration of the target object,
A seismic isolation device or a vibration control device. N attenuation coefficients cj (j = 1 to N) substantially match N optimal attenuation coefficients,
Here, the N optimum damping coefficients are expressed by a mass system having a structure in which the N viscous mass dampers with springs and the main frame support the target structure in parallel on the basis of the support. The ratio p / ωs between the vibration frequency p obtained by numerical analysis of the mass system and the natural frequency ωs of one vibration mode displaced in a specific direction of the target structure is taken as the horizontal axis, In the graph with the response magnification as the vertical axis, assuming that the N attenuation coefficients c match the N optimum attenuation coefficients, the values at the (N + 1) fixed points are substantially substantially N attenuation coefficients cj that are maximal,
The seismic isolation device or the vibration damping device according to claim 7, wherein the seismic isolation device or the vibration damping device is provided. The damper natural frequency ωj of each of the N damper natural frequencies ωj (j = 1 to N) substantially matches N predetermined values,
Here, the N predetermined values are expressed in a mass system that has a structure in which the N viscous mass dampers with a spring and a main frame support the target structure in parallel on the basis of a support. The ratio p / ωs between the vibration frequency p obtained by numerical analysis of the mass system and the natural frequency ωs of one vibration mode displaced in a specific direction of the target structure is taken as the horizontal axis, and the response of the target structure Assuming that the N damper natural frequencies ωj (j = 1 to N) coincide with N predetermined values in the graph with the magnification as the vertical axis , the natural frequency ωs is the minimum natural frequency ωmin. The maximum value Pmax on the line indicating the relationship between the response magnification and the ratio p / ωs when taking a value between the maximum natural frequency ωmax and the natural frequency ωs is the minimum natural frequency ωmin. The natural vibration is lower than the maximum value Pmax when ωs is N number of the damper natural frequency ωj be lower than the maximum value Pmax when the maximum natural frequency .omega.max,
The seismic isolation device or the vibration damping device according to any one of claims 7 to 9. A seismic isolation device or a vibration control device for damping the vibration of the target structure supported by the main frame on the basis of the support,
N spring mass viscous dampers that are 2 or more
Prepared,
An inertial connection element that converts a relative displacement in a specific direction generated by vibration of the viscous mass damper with a spring into a rotation amount of the rotating body, and an elastic reaction force that acts along the specific direction corresponding to the relative displacement in the specific direction. A system in which the inertia connecting element and the damper element are connected in parallel with a spring element that generates a damping force and a damper element that generates a damping resistance acting along a specific direction corresponding to a relative speed in a specific direction. A system in which a certain viscous mass damper and the spring element are connected in series,
The spring-equipped viscous mass damper has a damper natural frequency ω corresponding to an elastic coefficient kb of the spring element and an apparent inertia mass m with respect to a relative acceleration in a specific direction of the inertia connecting element and the damping resistance of the damper element. Having a damping coefficient c corresponding to the value divided by the relative velocity,
Or
The spring-attached 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 rotating body. A viscous mass damper having a viscous fluid sealed in a gap and a spring element having an elastic body, and the viscous mass damper and the spring element are connected in series,
An elastic coefficient kb which is a value obtained by dividing a reaction force generated when the spring-equipped viscous mass damper displaces the spring element by a relative distance in the linear motion direction, and the linear motion shaft of the viscous mass damper. To the apparent inertia mass m, which is a value obtained by dividing the reaction force generated by the inertial force of the rotating body 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. When the corresponding damper natural frequency ω and the linear motion shaft of the viscous mass damper are linearly moved at a constant relative speed, the reaction force generated by the damping resistance force of the viscous fluid acting in the linear motion direction is the relative force. A damping coefficient c corresponding to the value divided by the speed,
One of the
Here, the elastic coefficient kb, the apparent inertia mass m, and the damper natural frequency ω are in the following relationship:

The N viscous mass dampers with springs each having different damper natural frequencies ωj (j = 1 to N) are subject to relative displacement corresponding to the relative displacement in a specific direction of the target structure. Attached to each structure,

A viscous mass damper set with a first spring having N viscous mass dampers with N first springs, which are N or more viscous mass dampers with springs;
A second spring-attached viscous mass damper set comprising N second spring-attached viscous mass dampers that are N or more of said spring-attached viscous mass dampers;
With
The damper natural frequencies ωj (j = 1 to N) of the N first viscous mass dampers with springs are different from each other,
The damper natural frequency ωj (j = 1 to N) of the N second viscous mass dampers with springs is different from each other,
The damping coefficients cj (j = 1 to N) of the N first viscous mass dampers with springs are different from each other,
The damping coefficients cj (j = 1 to N) of the N second viscous mass dampers with springs are different from each other,
The damper natural frequency ωj (j = 1 to N) of each of the N number of viscous mass dampers with the first spring and the damper natural frequency ωj (j of each of the N number of viscous mass dampers with the second spring) = 1 to N) approximately matches each pair,
The damping coefficient cj (j = 1 to N) of each of the N first viscous mass dampers with springs (j = 1 to N) and the N viscous mass dampers with second springs (j = 1 to N) ) Of each of the attenuation coefficients cj (j = 1 to N) substantially coincide with each other,
N pieces of viscous mass dampers with first springs and N pieces of viscous mass dampers with second springs are symmetric with respect to each other with respect to the rigid center of the target structure, or the rigidity of the target structure. N pieces of viscous mass dampers with first springs and N pieces of viscous mass dampers with second springs are used as a support and target structure so that each pair is symmetrical with respect to a virtual line passing through the center. Attached to each other or inside the target structure,
A seismic isolation device or a vibration control device. A seismic isolation device or a vibration control device for damping the vibration of the target structure supported by the main frame on the basis of the support,
N spring mass viscous dampers that are 2 or more
Prepared,
An inertial connection element that converts a relative displacement in a specific direction generated by vibration of the viscous mass damper with a spring into a rotation amount of the rotating body, and an elastic reaction force that acts along the specific direction corresponding to the relative displacement in the specific direction. A system in which the inertia connecting element and the damper element are connected in parallel with a spring element that generates a damping force and a damper element that generates a damping resistance acting along a specific direction corresponding to a relative speed in a specific direction. A system in which a certain viscous mass damper and the spring element are connected in series,
The spring-equipped viscous mass damper has a damper natural frequency ω corresponding to an elastic coefficient kb of the spring element and an apparent inertia mass m with respect to a relative acceleration in a specific direction of the inertia connecting element and the damping resistance of the damper element. Having a damping coefficient c corresponding to the value divided by the relative velocity,
Or
The spring-attached 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 rotating body. A viscous mass damper having a viscous fluid sealed in a gap and a spring element having an elastic body, and the viscous mass damper and the spring element are connected in series,
An elastic coefficient kb which is a value obtained by dividing a reaction force generated when the spring-equipped viscous mass damper displaces the spring element by a relative distance in the linear motion direction, and the linear motion shaft of the viscous mass damper. To the apparent inertia mass m, which is a value obtained by dividing the reaction force generated by the inertial force of the rotating body 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. When the corresponding damper natural frequency ω and the linear motion shaft of the viscous mass damper are linearly moved at a constant relative speed, the reaction force generated by the damping resistance force of the viscous fluid acting in the linear motion direction is the relative force. A damping coefficient c corresponding to the value divided by the speed,
One of the
Here, the elastic coefficient kb, the apparent inertia mass m, and the damper natural frequency ω are in the following relationship:

The N viscous mass dampers with springs each having different damper natural frequencies ωj (j = 1 to N) are subject to relative displacement corresponding to the relative displacement in a specific direction of the target structure. Attached to the structure,
A plurality of sets of spring-attached viscous mass dampers each having two or more N spring-attached viscous mass dampers;
The damper natural frequency ωj (j = 1 to N) of the N viscous mass dampers with springs belonging to the same set of viscous mass dampers with springs is different from each other,
The damping coefficients cj (j = 1 to N) of the N viscous mass dampers with springs belonging to the same set of viscous mass dampers with springs are different from each other,
A plurality of the above-mentioned spring-attached viscous mass dampers obtained by selecting and combining one spring-attached viscous mass damper belonging to a different set from the whole of the above-mentioned N pieces of spring-attached viscous mass dampers belonging to a plurality of spring-attached viscous mass damper sets Each of the damper natural frequencies ωj (j = 1 to N) substantially coincides with each other,
A plurality of the above-mentioned spring-attached viscous mass dampers obtained by selecting and combining one spring-attached viscous mass damper belonging to a different set from the whole of the above-mentioned N pieces of spring-attached viscous mass dampers belonging to a plurality of spring-attached viscous mass damper sets Each of the attenuation coefficients cj (j = 1 to N) substantially matches with each other,
Each rotational moment acting around the rigid core of the target structure is canceled out by each group by the reaction force generated by each of N spring mass viscous dampers belonging to different sets of spring mass viscous dampers. In this way, N pieces of spring-loaded viscous mass dampers belonging to a plurality of sets of spring-attached viscous mass damper sets are respectively attached between the support and the target structure or inside the target structure.
A seismic isolation device or a vibration control device.

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