JP2016148449A - Vibration suppression device of structure - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vibration suppression device of a structure, which can properly suppress vibration when vibration of the structure is relatively small, and, when vibration of the structure is relatively large, which can prevent damage of the vibration suppression device and the structure due to excessive displacement of an additional vibration system with a relatively simple configuration.SOLUTION: A vibration suppression device 1 includes a mass body 2 connected to a structure R through a transmission member 3 having elasticity, and a variable attenuation damper 6. The attenuation coefficient of the variable attenuation damper 6, when a piston is positioned in a predetermined first outside section, is made larger than that in a case of being positioned in a predetermined inside section. The mass body 2, the transmission member 3 and the variable attenuation damper 6 constitute an additional vibration system. The specification of the additional vibration system is set so that when the piston is positioned in the inside section during vibration of the structure R, the eigen frequency of the additional vibration system synchronizes with the eigen frequency of the structure R.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a structure vibration suppressing device for suppressing the vibration of a structure, and more particularly to a structure vibration suppressing device including a dynamic vibration absorber having a variable damping damper.

  Conventionally, for example, a device disclosed in Non-Patent Document 1 is known as a vibration suppressing device for this type of structure. This vibration suppression device is configured as a dynamic vibration absorber applied to a high-rise building, and includes a weight connected to the building in a pendulum shape via a wire, and an oil damper having a speed limiting mechanism. The speed limiting mechanism has a hydraulic circuit connected to an oil damper and an oil tank, and the hydraulic circuit includes a first system including a first pressure regulating valve and a first spool valve, a second pressure regulating valve, and the like. A second system and a third system including an accumulator and a second spool valve are used.

  In the oil damper having the above configuration, when the input speed (hereinafter referred to as “damper input speed”) is lower than a predetermined speed, both the first pressure regulating valve of the first system and the second pressure regulating valve of the second system described above are used. Is activated, the damping coefficient of the oil damper (hereinafter referred to as “damper damping coefficient”) becomes the first predetermined value. When the damper input speed reaches a predetermined speed, only the second pressure regulating valve operates by closing the first spool valve, so that the damper damping coefficient increases rapidly, and when the damper input speed is higher than the predetermined speed, the damper The attenuation coefficient becomes a very large second predetermined value. The third system functions to operate both the first and second pressure regulating valves again and return the damping coefficient to the first predetermined value when the damper input speed once exceeds the predetermined speed and then decreases. . In this conventional vibration suppression device, the damper damping coefficient is changed as described above to prevent an excessive displacement of the weight during a large earthquake.

Naoki Kano, Takeshi Nakai, Ryusuke Fukuda, Masaya Kusunoki, Haruhiko Kurino “Development of TMD for Stroke Control Functions for High-rise Buildings (Part 2) Examination of TMD Components Using High-Rise Building Models” ) September 2014, pages 751 to 752

  As described above, the conventional vibration suppression device has a hydraulic circuit including the first and second pressure regulating valves and the first and second spool valves as a speed limiting mechanism for changing the damper damping coefficient. Therefore, the configuration is very complicated. In addition, the damper damping coefficient does not increase unless the damper input speed reaches the predetermined speed, so the damper damping coefficient may not increase even if the displacement of the weight becomes very large due to the large displacement due to the vibration of the building. In that case, the entire vibration suppressing device including the weight and the structure may be damaged.

  The present invention has been made to solve the above-described problems. When the vibration of the structure is relatively small, the vibration of the structure can be appropriately suppressed and the vibration of the structure is relatively large. In some cases, an object of the present invention is to provide a vibration suppressing device and a structure vibration suppressing device that can prevent damage to the structure due to excessive displacement of the additional vibration system and a structure with a relatively simple configuration.

  In order to achieve the above object, the invention according to claim 1 is a structure vibration suppressing device for suppressing vibration of a structure, and is connected to the structure via an elastic transmission member. The variable damping damper includes a cylinder coupled to one of the structure and the mass body, and is provided in the cylinder so as to be movable in the axial direction. The first fluid chamber is disposed in the cylinder. And the second fluid chamber, and is connected to the other of the structure and the mass body, and is filled in the first and second fluid chambers with a piston located at a predetermined neutral position when the structure is not vibrating. When the piston is located in a predetermined inner section including a neutral position, the inner communication passage bypassing the piston and allowing the first and second fluid chambers to communicate with each other, and the piston And the inner section in the cylinder And an outer communication passage that allows the first and second fluid chambers to communicate with each other when positioned in a predetermined section including a predetermined first outer section on both outer sides in the axial direction. (1) The damping coefficient is larger when positioned in the outer section than when positioned in the inner section, and the mass body, the transmission member, and the variable damping damper constitute an additional vibration system. The specifications of the additional vibration system are set so that the natural frequency of the additional vibration system is synchronized with the natural frequency of the structure when the piston is located in the inner section during vibration of the structure. It is characterized by being.

  According to this configuration, the additional vibration system is configured by the transmission member, the mass body connected to the structure via the transmission member, and the variable damping damper, and the additional vibration system vibrates with the vibration of the structure. By (resonating), the vibration of the structure is absorbed and suppressed. The variable damping damper is configured as a so-called passive type variable damping damper. Specifically, the variable damping damper includes a cylinder connected to one of the structure and the mass body, and a piston connected to the other of the structure and the mass body. Have. The cylinder is partitioned into a first fluid chamber and a second fluid chamber by a piston and filled with a working fluid, and the piston is located at a predetermined neutral position when the structure is not vibrating. .

  The variable damping damper further includes an inner communication path and an outer communication path, and when the piston is located in a predetermined inner section including the neutral position, the first and second fluid chambers are Are communicated with each other through an inner communication passage that bypasses the inner passage. When the piston is located in a predetermined section including the inner section and a predetermined first outer section on both outer sides in the axial direction, the first and second fluid chambers are disposed via the outer communication path. Communicate with each other.

  In the variable damping damper having the above configuration, the piston reciprocates in the cylinder as the structure vibrates. When the vibration of the structure is relatively small, the piston reciprocates in the inner section, and the working fluid pressed by the moving piston passes through both the inner communication path and the outer communication path. Two fluid chambers flow from one to the other. As described above, when the vibration of the structure is relatively small, and the piston is located in the inner section, the damping coefficient of the variable damping damper is relatively small. When the vibration of the structure becomes relatively large, the piston reciprocates in the first outer section beyond the inner section, and the working fluid pressed by the piston moving in the first outer section is The fluid flows from one of the first and second fluid chambers to the other through the outer communication path, not through the inner communication path. As described above, when the vibration of the structure is relatively large, and the piston is located in the first outer section, the damping coefficient of the variable damping damper becomes larger than when the piston is located in the inner section.

  Further, according to the above-described configuration, the specifications of the additional vibration system having the mass body, the transmission member, and the variable damping damper are determined when the piston is positioned in the inner section during the vibration of the structure, that is, the structure. Is set so that the natural frequency of the additional vibration system is synchronized with the natural frequency of the structure. Therefore, when the vibration of the structure is relatively small, the vibration of the structure can be appropriately suppressed. In addition, as described above, when the vibration of the structure is relatively large, a greater damping force of the variable damping damper connected to the mass body and the structure can be obtained, resulting in an excessive displacement of the additional vibration system. It is possible to prevent damage to the vibration suppressing device and the structure. Further, unlike the above-described conventional vibration suppression device, a relatively simple configuration of an inner communication path and an outer communication path rather than a complicated hydraulic circuit composed of the first and second pressure regulating valves and the first and second spool valves. Thus, the above-described effect can be obtained.

  The invention according to claim 2 is the vibration suppression device for a structure according to claim 1, wherein the transmission member is attached to the structure, the mass body is supported in a state of being placed on the transmission member, and the mass The abutting body provided integrally with one of the body and the structure, and the other of the mass body and the structure are provided so as to be immovable in the horizontal direction and movable in the vertical direction. Detecting a displacement parameter that represents the horizontal displacement of the mass body with respect to the structure due to vibration. When the displacement of the mass body represented by the detected displacement parameter reaches a predetermined displacement during the vibration of the structure and the displacement parameter detecting means, the contact body is brought into contact with the contacted body. And a control means for controlling the pressing mechanism. To.

  According to this configuration, the mass body is supported in a mounted state on the transmission member attached to the structure, and the abutted body is integrally provided on one of the mass body and the structure. The contact body is provided on the other of the mass body and the structure so as not to move in the horizontal direction and to be movable in the vertical direction. The abutting body faces the abutted body with a space in the vertical direction, and the abutting body is pressed toward the abutted body by the pressing mechanism. In addition, a displacement parameter representing the horizontal displacement of the mass body relative to the structure due to vibration is detected by the displacement parameter detection means, and during the vibration of the structure, the displacement of the mass body represented by the detected displacement parameter is a predetermined displacement. When the pressure is reached, the pressing mechanism is controlled by the control means so that the contact body comes into contact with the contacted body.

  As described above, when the structure is not vibrating, or when the vibration of the structure is relatively small and the horizontal displacement of the mass body relative to the structure is small, the contact body is not pressed by the pressing mechanism. When the vibration of the structure becomes relatively large and the displacement of the mass body reaches a predetermined displacement without being in contact with the contacted body, it is contacted with the contacted body by being pressed by the pressing mechanism. . Thus, when the vibration of the structure is relatively large, in addition to the greater damping force of the variable damping damper described in the description of the invention according to claim 1, the resistance caused by the friction between the abutting body and the abutted body More power is gained. Therefore, the effect of the invention according to claim 1, that is, the vibration suppression device and the structure due to the excessive displacement of the additional vibration system (displacement of the mass body with respect to the structure) when the vibration of the structure is relatively large. The effect that damage can be prevented can be obtained with certainty.

  In order to achieve the above object, the invention according to claim 3 is a vibration suppressing device for a structure for suppressing the vibration of the structure erected on the foundation, comprising a rotatable rotating mass, a foundation and a structure. The relative displacement between the predetermined first part and the second part in the system including the object is transmitted via the elastic transmission member, and the transmitted relative displacement between the first and second parts. A power conversion mechanism that performs a power conversion transmission operation that transmits the rotation to a rotary mass in a state of being converted into a rotational motion, and a variable damping damper, and the variable damping damper includes a cylinder coupled to the first portion, It is provided so as to be movable in the axial direction, divides the inside of the cylinder into a first fluid chamber and a second fluid chamber, is connected to the second portion, and is located at a predetermined neutral position when the structure is not vibrating. Filling the piston and the first and second fluid chambers When the piston is positioned in a predetermined inner section including a neutral position, the inner communication passage bypassing the piston and causing the first and second fluid chambers to communicate with each other; and the piston includes the inner section And an outer communication passage that allows the first and second fluid chambers to communicate with each other when the first and second fluid chambers are located in a predetermined section including both predetermined first outer sections on both outer sides in the axial direction than the inner section in the cylinder; When the piston is located in the first outer section, the damping coefficient is larger than when the piston is located in the inner section, and the rotary mass, the transmission member, and the variable damping damper are The additional vibration system is configured so that the natural frequency of the additional vibration system is the natural frequency of the structure when the piston is positioned in the inner section during vibration of the structure. Set to tune to And wherein the Rukoto.

  According to this configuration, the relative displacement between the predetermined first part and the second part in the system including the structure is transmitted to the power conversion mechanism via the transmission member. The power conversion mechanism performs a power conversion transmission operation in which the transmitted relative displacement between the first and second parts is converted to a rotational motion and transmitted to the rotary mass, whereby the rotary mass rotates. Furthermore, an additional vibration system is configured by the rotating mass, the transmission member, and the variable damping damper, and the additional vibration system absorbs and suppresses the vibration of the structure by vibrating (resonating) with the vibration of the structure. To do. In this case, the effect of suppressing the vibration of the structure by the additional vibration system is enhanced by obtaining the rotation inertial mass effect by the rotation mass.

  Similar to the variable damping damper according to the first aspect of the present invention, the variable damping damper is configured as a so-called passive variable damping damper. Specifically, the variable damping damper has a cylinder connected to the first part, a piston connected to the second part while being provided in the cylinder so as to be movable in the axial direction. The cylinder is partitioned into a first fluid chamber and a second fluid chamber by a piston and filled with a working fluid, and the piston is located at a predetermined neutral position when the structure is not vibrating. .

  The variable damping damper further includes an inner communication path and an outer communication path, and when the piston is located in a predetermined inner section including the neutral position, the first and second fluid chambers are Are communicated with each other through an inner communication passage that bypasses the inner passage. When the piston is located in a predetermined section including the inner section and a predetermined first outer section on both outer sides in the axial direction, the first and second fluid chambers are disposed via the outer communication path. Communicate with each other.

  As is apparent from the above configuration, the variable damping damper according to the present invention has the same basic configuration as the variable damping damper according to the first aspect, except that the connection destination of the cylinder and the piston is different. is there. Therefore, in the variable damping damper according to the present invention, the vibration of the structure is relatively small, so that when the piston is located in the inner section, the damping coefficient of the variable damping damper is relatively small. Further, when the vibration of the structure is relatively large, and the piston is located in the first outer section, the damping coefficient of the variable damping damper becomes larger than when the piston is located in the inner section.

  Further, according to the above-described configuration, the specifications of the additional vibration system having the rotating mass, the transmission member, and the variable damping damper are determined when the piston is positioned in the inner section during the vibration of the structure, that is, the structure. Is set so that the natural frequency of the additional vibration system is synchronized with the natural frequency of the structure. Therefore, similarly to the invention according to claim 1, when the vibration of the structure is relatively small, the vibration of the structure can be appropriately suppressed. In addition, as described above, when the vibration of the structure is relatively large, a greater damping force of the variable damping damper connected to the first and second portions can be obtained, so that the displacement of the additional vibration system is excessively increased. It is possible to prevent the vibration suppressing device and the structure from being damaged. Further, unlike the above-described conventional vibration suppression device, a relatively simple configuration of an inner communication path and an outer communication path rather than a complicated hydraulic circuit composed of the first and second pressure regulating valves and the first and second spool valves. Thus, the above-described effect can be obtained.

  According to a fourth aspect of the present invention, in the vibration suppressing device for a structure according to the third aspect, at least one of the cylinder and the piston is connected to at least one of the first and second parts to which the at least one is connected. The power conversion mechanism performs the power conversion transmission operation while the relative displacement between the first and second parts is transmitted via the transmission member, the cylinder, the piston, and the working fluid. Thus, the flow of the working fluid in the inner communication path and the outer communication path is transmitted to the rotary mass in a state of being converted into a rotary motion.

  According to this configuration, at least one of the cylinder and the piston is connected to at least one of the first and second parts to which the at least one is connected via the transmission member. In the power conversion mechanism, the relative displacement between the first and second parts is transmitted through the transmission member, the cylinder, the piston, and the working fluid, and the power conversion transmission operation is performed in the inner communication path and the outer side. The flow of the working fluid in the communication path is converted into a rotary motion and transmitted to the rotary mass. As described above, since the rotary mass, the power conversion mechanism and the transmission member, and the variable damping damper are not provided separately from each other, but are provided integrally with each other, the overall size of the vibration suppression device can be reduced. Can do.

  According to a fifth aspect of the present invention, in the vibration suppression device for a structure according to any one of the first to fourth aspects, when the pressure of the working fluid in the first fluid chamber reaches the first predetermined pressure in the piston. A first relief valve that opens and communicates the first and second fluid chambers, and opens when the pressure of the working fluid in the second fluid chamber reaches a second predetermined pressure; A second relief valve is provided for communicating the chambers with each other, and bypasses the piston when the piston is positioned in a predetermined second outer section on both outer sides in the axial direction than the first outer section in the cylinder. And the communication passage for communicating the first and second fluid chambers with each other, and the working fluid is provided when the piston moves toward the side opposite to the neutral position in the second outer section. One of the first and second fluid chambers via the communication path When the piston is moving toward the neutral position side in the second outer section, the working fluid is moved from the other of the first and second fluid chambers through the communication path. And a check valve that allows fluid to flow.

  According to this configuration, the first and second relief valves are provided in the piston of the variable damping damper, and when the pressure of the working fluid in the first fluid chamber reaches the first predetermined pressure, the first relief valve The second relief valve is opened when the pressure of the working fluid in the second fluid chamber reaches the second predetermined pressure, and causes the first and second fluid chambers to communicate with each other. The variable damping damper has a communication path for allowing the first and second fluid chambers to communicate with each other when the piston is positioned in a predetermined second outer section on both outer sides in the axial direction than the first outer section. A check valve is provided in the communication path. The check valve allows the flow of the working fluid through the communication path from one of the first and second fluid chambers to the other when the piston moves toward the side opposite to the neutral position in the second outer section. While preventing, when the piston is moving toward the neutral position side in the second outer section, the flow of the working fluid is allowed through the communication path from the other of the first and second fluid chambers to one side.

  As described above, when the piston is moving toward the side opposite to the neutral position in the second outer section because the vibration of the structure is very large, the first and second fluid chambers are connected to the inner communication path and the outer side described above. When the pressure of the working fluid in the first or second fluid chamber reaches the first or second predetermined pressure, the first or second relief valve described above is not communicated with each other via the communication passage and the communication passage. The valves are communicated with each other by opening the valve. Accordingly, the working fluid pressed by the moving piston flows from one of the first and second fluid chambers to the other via the first or second relief valve. As described above, since the damping force of the variable damping damper can be obtained when the vibration of the structure is very large, the vibration suppressing device and the structure are prevented from being damaged due to excessive displacement of the additional vibration system. be able to.

  Further, when the piston is moving toward the neutral position side in the second outer section because the vibration of the structure is very large, the working fluid in the other of the first and second fluid chambers is passed through the communication path. Since it can escape to one of the first and second fluid chambers, it is possible to prevent the piston from returning to the neutral position.

  According to a sixth aspect of the present invention, in the vibration suppressing device for a structure according to the second aspect, the control means is configured such that the displacement of the mass body represented by the displacement parameter is equal to or greater than a predetermined displacement during the vibration of the structure. Further, the larger the displacement of the mass body, the greater the pressing force of the pressing mechanism is controlled.

  According to this configuration, when the displacement of the mass body represented by the displacement parameter is greater than or equal to the predetermined displacement during the vibration of the structure, the greater the displacement of the mass body, the greater the pressing force of the pressing mechanism. To be controlled. Accordingly, when the displacement of the mass body is greater than or equal to a predetermined displacement due to the relatively large vibration of the structure, the greater the displacement of the mass body, the greater the resistance caused by the friction between the contact body and the contacted body. Since the force can be obtained, the effect of the invention according to claim 1, that is, the vibration suppressing device and the structure are prevented from being damaged due to excessive displacement of the additional vibration system when the vibration of the structure is relatively large. The effect that it is possible can be obtained more effectively.

It is a figure which shows roughly the vibration suppression apparatus by 1st Embodiment of this invention with the rack warehouse to which this is applied. It is a perspective view which fractures | ruptures and shows a part of transmission member of the vibration suppression apparatus of FIG. It is a perspective view which fractures | ruptures and shows a part of support body of the vibration suppression apparatus of FIG. It is sectional drawing which shows schematically the variable damping damper of the vibration suppression apparatus of FIG. It is a figure which shows schematically the rack warehouse of FIG. 1, the mass body of a vibration suppression device, and a variable damping damper. FIG. 5 is a cross-sectional view schematically showing the variable damping damper of FIG. 4 when a piston is located at an end of a second joint section. FIG. 4 is a diagram illustrating the transmission member of FIG. 2 and the support of FIG. 3 when (a) the rack warehouse is not vibrating, and (b) when the rack warehouse is relatively vibrated. (A) The figure which shows the relationship between the deformation amount of the horizontal direction of the transmission member of FIG. 2, and its resistance force, (b) The horizontal direction deformation amount of the transmission member of FIG. 2, and the contact plate and slip of FIG. The figure which shows the relationship with the frictional force between board | plates, (c) Sum total of the deformation amount of the horizontal direction of the transmission member of FIG. 2, the resistance force of the transmission member of FIG. 2, and the frictional force between the contact plate of FIG. It is a figure which shows the relationship. It is sectional drawing which shows schematically the variable damping damper by the 1st modification of 1st Embodiment. It is sectional drawing which shows schematically the variable damping damper by the 2nd modification of 1st Embodiment. It is a figure which shows roughly the vibration suppression apparatus by 2nd Embodiment of this invention with a part of building which applied this. FIG. 12 is a cross-sectional view schematically showing a variable damping mass damper of the vibration suppression device of FIG. 11. It is sectional drawing which shows schematically the variable damping mass damper of FIG. 12 in case a piston is located in the end of a joint area. It is a figure which shows roughly the vibration suppression apparatus by the modification of 2nd Embodiment with a part of building which applied this. It is sectional drawing which shows schematically the variable damping mass damper by the modification of 2nd Embodiment. It is a figure which shows roughly the vibration suppression apparatus by 3rd Embodiment of this invention with the rack warehouse to which this is applied. FIG. 17 is an enlarged view schematically showing a flat jack, a support body, and the like of the vibration suppressing device of FIG. 16 during the jack down mode. FIG. 17 is an enlarged view schematically showing a flat jack, a support body, and the like of the vibration suppressing device of FIG. 16 during the jack-up mode. It is a block diagram which shows the control apparatus etc. of the vibration suppression apparatus of FIG. It is a flowchart which shows the process performed by the control apparatus of FIG.

  Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the drawings. The vibration suppressing device 1 according to the first embodiment of the present invention shown in FIG. 1 is for suppressing the vibration of the rack warehouse R (mainly horizontal vibration), and is provided at the upper end of the rack warehouse R. Yes. As shown in FIG. 1, the vibration suppression device 1 includes a mass body 2, a plurality of transmission members 3, a contact plate 4, a support body 5, and a variable damping damper 6. The mass body 2 is made of a material having a relatively large specific gravity, for example, iron, and is formed in a rectangular parallelepiped shape. In FIG. 1, reference numerals of detailed components are omitted for convenience.

  As shown in FIG. 2, each transmission member 3 is configured in the same manner as a general rubber-type seismic isolation device, and between a pair of upper and lower rectangular plate-like flanges 11, 11 and both flanges 11, 11. In addition, a plurality of disk-shaped inner rubbers 12 laminated integrally with each other and a cylindrical covering rubber 13 covering the outer surface of the inner rubber 12 are provided. The internal rubber 12 is attached to the upper and lower flanges 11 and 11 via upper and lower internal steel plates 14 and 14, respectively. In FIG. 2, for the sake of convenience, a part of the internal rubber 12 is omitted, and cross sections of the internal rubber 12, the covering rubber 13, and the internal steel plates 14 and 14 are not hatched.

  Each of the four corners of each flange 11 is formed with three mounting holes 11a penetrating in the vertical direction, and bolts (not shown) are inserted into the respective mounting holes 11a. The bolt inserted into the mounting hole 11a of the upper flange 11 is screwed into the bottom surface of the mass body 2, and the bolt inserted into the mounting hole 11a of the lower flange 11 is screwed into the upper end of the rack warehouse R. It is. As described above, the mass body 2 is supported by the transmission member 3 attached to the upper end portion of the rack warehouse R.

  Each of the plurality of contact plates 4 is made of a material having a stable friction coefficient, such as stainless steel, and is attached to the bottom surface of the mass body 2. The plurality of supports 5 are provided corresponding to the plurality of contact plates 4. As shown in FIG. 3, each of the plurality of supports 5 includes a disc-shaped sliding plate 21, a rectangular plate-shaped flange 22, and a circle that is laminated integrally between the sliding plate 21 and the flange 22. A plurality of plate-like internal rubbers 23 and a cylindrical covering rubber 24 covering the outer surface of the internal rubber 23 are provided. The internal rubber 23 is attached to the sliding plate 21 and the flange 22 via upper and lower internal steel plates 25 and 25, respectively. The sliding plate 21 is made of a material having a stable friction coefficient, for example, a fluororesin. In FIG. 3, for convenience, a part of the internal rubber 23 and hatching of the sliding plate 21, the internal rubber 23, the covering rubber 24, and the internal steel plates 25, 25 are omitted.

  Each of the four corners of the flange 22 is formed with three attachment holes 22a penetrating in the vertical direction, and bolts (not shown) are inserted into the attachment holes 22a. These bolts are screwed into the upper end portion of the rack warehouse R, whereby the support 5 is attached to the upper end portion of the rack warehouse R. As shown in FIGS. 1 and 7A, when the rack warehouse R is not vibrating, the sliding plate 21 of the support 5 faces the contact plate 4 in the vertical direction with a predetermined distance DI. doing. A method for setting the predetermined interval DI will be described later.

  Further, each of the plurality of variable damping dampers 6 is configured as a so-called passive type variable damping damper, and as shown in FIG. And a rod 33 provided integrally with the piston 32 and partially accommodated in the cylinder 31 so as to be movable in the axial direction. Hereinafter, the variable damping damper 6 will be described with the left side and the right side in FIG. 4 as “left” and “right”, respectively.

  The cylinder 31 includes a left wall 31a and a right wall 31b facing each other, and a peripheral wall 31c provided integrally between the both 31a and 31b. The oil chamber defined by the left and right walls 31a and 31b and the peripheral wall 31c is divided into a first oil chamber 31d on the left side and a second oil chamber 31e on the right side by the piston 32, and both oil chambers 31d and 31e are separated. Is filled with hydraulic oil HF made of silicon oil. Further, a rod guide hole 31f penetrating in the left-right direction (axial direction) is formed at the radial center of the right wall 31b, and a seal 41 is provided in the rod guide hole 31f. Furthermore, the left wall 31a is integrally provided with a convex portion 31g protruding leftward, and the convex portion 31g is provided with a first fixture FL1 via a universal joint.

  The rod 33 is inserted into the rod guide hole 31f via the seal 41, extends in the axial direction, and is movable in the axial direction with respect to the cylinder 31, and its left end is attached to the piston 32. Yes. Moreover, the 2nd fixture FL2 is provided in the right end part of the rod 33 via the universal joint.

  The piston 32 is formed in a columnar shape, and a seal 42 is provided on the peripheral surface thereof. When the rack warehouse R is not vibrating, as shown in FIG. Located in the neutral position. The neutral position is not limited to this, and may be a position on the left side or the right side of the center of the cylinder 31 in the axial direction. In addition, a plurality of holes penetrating in the axial direction are formed in the radially outer end of the piston 32 (only two are shown), and the first relief valve 43 and the second relief valve are formed in these holes. 44 is provided.

  The first relief valve 43 is configured by a valve body and a spring that biases the valve body toward the valve closing side, and the hydraulic oil HF in the first oil chamber 31d is moved by the movement of the piston 32 accompanying the vibration of the rack warehouse R. The valve is opened when the pressure reaches a predetermined upper limit. As a result, the first and second oil chambers 31d and 31e communicate with each other, thereby preventing the pressure of the hydraulic oil HF in the first oil chamber 31d from becoming excessive. Similar to the first relief valve 43, the second relief valve 44 is configured by a valve body and a spring that biases the valve body toward the valve closing side, and the second oil is moved by the movement of the piston 32 accompanying the vibration of the rack warehouse R. The valve is opened when the pressure of the hydraulic oil HF in the chamber 31e reaches the upper limit. As a result, the first and second oil chambers 31d and 31e communicate with each other, thereby preventing the pressure of the hydraulic oil HF in the second oil chamber 31e from becoming excessive.

  The variable damping damper 6 further includes a first communication pipe 34, a second communication pipe 35, a third communication pipe 36, and fourth communication pipes 37L and 37R that are connected to the cylinder 31 and have a circular cross section. The cross-sectional area (area of the surface orthogonal to the axial direction) of the first to fourth communication pipes 34 to 36, 37L, 37R is set to a value smaller than the cross-sectional area of the cylinder 31 (area of the surface orthogonal to the axial direction). The cross-sectional areas of the first to third communication pipes 34 to 36 are set to the same value.

  The first communication pipe 34 bypasses the piston 32 when the piston 32 is positioned in the predetermined first section IN1 including the neutral position in the cylinder 31, and the first and second oil chambers 31d, 31e. Are connected to each other. More specifically, the first communication pipe 34 is arranged so that the inner wall surface on the neutral position side at the connection portion with the cylinder 31 is flush with the end of the first section IN1. In the first embodiment, the center in the axial direction of the first section IN1 coincides with the neutral position, but may be shifted.

  In the second communication pipe 35, the piston 32 is located in a first joint section IU1 including a first section IN1 and a predetermined second section IN2 on both outer sides in the axial direction of the first section IN1 in the cylinder 31. The first and second oil chambers 31d and 31e are provided to communicate with each other when the piston 32 is bypassed. More specifically, the second communication pipe 35 is arranged so that the inner wall surface on the neutral position side at the connection portion with the cylinder 31 is flush with the end of the first joint section IU1. In the first embodiment, the length in the axial direction of the second section IN2 on the left side and that of the second section IN2 on the right side are the same as each other, but may be different.

  Further, in the third communication pipe 36, the piston 32 has a first section IN1 and a second section IN2, and a predetermined third section IN3 on both outer sides in the axial direction of the second section IN2 in the cylinder 31. When the first joint section IU2 is located, the piston 32 is bypassed and the first and second oil chambers 31d and 31e are communicated with each other. More specifically, the third communication pipe 36 is disposed such that the inner wall surface on the neutral position side at the connection portion with the cylinder 31 is flush with the end of the second joint section IU2. In the first embodiment, the length in the axial direction of the left third section IN3 and that of the right third section IN3 are the same as each other, but may be different.

  The fourth communication pipes 37L and 37R are constituted by a pair of left and right communication pipes, and the piston 32 is arranged in a predetermined fourth section IN4 on the outermost outer side in the axial direction from the third section IN3 in the cylinder 31. When located, the piston 32 is bypassed, and the first and second oil chambers 31d and 31e are provided in communication with each other. More specifically, as shown in FIG. 6, the fourth communication pipe 37L on the left side has an inner wall surface on the neutral position side (right side) connected to the cylinder 31 of the second joint section IU2. It arrange | positions so that it may become flush with the wall surface of the neutral position side of piston 32 located in an end. Further, the left fourth communication pipe 37L has an inner wall surface on the opposite side to the neutral position at the connection portion on the opposite side (left side) to the cylinder 31 so as to be flush with the inner wall surface of the left wall 31a. Have been placed. The fourth communication pipe 37R on the right side is arranged symmetrically with the fourth communication pipe 37L on the left side, and the arrangement of the left fourth communication pipe 37L as described above is the same for the fourth communication pipe 37R on the right side. It is.

  In the first embodiment, the length in the axial direction of the left fourth section IN4 and that of the right fourth section IN4 are the same as each other, but may be different.

  Furthermore, check valves 45L and 45R are provided on the left and right fourth communication pipes 37L and 37R, respectively. The left check valve 45L is configured such that the hydraulic oil HF is pressed by the piston 32 when the piston 32 moves toward the side opposite to the neutral position (left side) in the fourth section IN4 on the left side. The flow from the first oil chamber 31d to the second oil chamber 31e through the four communication pipes 37L is prevented. In addition, the check valve 45L is connected to the fourth communication fluid when the hydraulic oil HF is pressed by the piston 32 when the piston 32 is moving toward the neutral position side (right side) in the fourth section IN4 on the left side. It is allowed to flow from the second oil chamber 31e to the first oil chamber 31d through the pipe 37L.

  The right check valve 45R is configured such that the hydraulic oil HF is pressed by the piston 32 when the piston 32 is moving toward the side opposite to the neutral position (right side) in the fourth section IN4 on the right side. The flow from the second oil chamber 31e to the first oil chamber 31d through the four communication pipes 37R is prevented. The check valve 45R is connected to the fourth communication fluid when the piston 32 is moving toward the neutral position side (left side) in the fourth section IN4 on the right side, and the hydraulic oil HF is pressed by the piston 32. It is allowed to flow from the first oil chamber 31d to the second oil chamber 31e via the pipe 37R.

  In addition, as shown in FIG. 5, the above-described first fixture FL1 of the variable damping damper 6 is attached to the first connecting member EN1, and the second fixture FL2 is attached to the second connecting member EN2, respectively. The connecting member EN1 is attached to the bottom surface of the mass body 2, and the second connecting member EN2 is attached to the upper end of the rack warehouse R. As described above, the variable damping damper 6 has the cylinder 31 connected to the mass body 2 and the piston 32 connected to the rack warehouse R together with the rod 33, and extends in the horizontal direction. In FIG. 5, for convenience, the first to fourth communication pipes 34 to 36, 37L, and 37R are omitted.

  In the vibration suppressing device 1 having the above configuration, the mass body 2, the transmission member 3, and the variable damping damper 6 constitute an additional vibration system, and the additional vibration system vibrates as the rack warehouse R vibrates ( By resonating, the vibration of the rack warehouse R is absorbed and suppressed. Further, the piston 32 of the variable damping damper 6 reciprocates in the cylinder 31 as the rack warehouse R vibrates. When the vibration of the rack warehouse R is relatively small, the piston 32 reciprocates in the first section IN1, and the hydraulic oil HF pressed by the moving piston 32 passes through the first to third communication pipes 34 to 36. Thus, the fluid flows from one of the first and second oil chambers 31d and 31e to the other.

  As described above, when the vibration of the rack warehouse R is relatively small, and the piston 32 is located in the first section IN1, the damping coefficient of the variable damping damper 6 is relatively small. Further, when the vibration of the rack warehouse R increases, the piston 32 reciprocates in the second section IN2 beyond the first section IN1, and the hydraulic oil HF pressed by the piston 32 moving in the second section IN2. Flows from one of the first and second oil chambers 31d, 31e to the other through the second and third communication pipes 35, 36, not through the first communication pipe 34. As described above, when the vibration of the rack warehouse R is relatively large, and the piston 32 is located in the second section IN2, the damping coefficient of the variable damping damper 6 is larger than that in the first section IN1. growing.

  When the vibration of the rack warehouse R further increases, the piston 32 reciprocates in the third section IN3 beyond the first and second sections IN1 and IN2, and is pressed by the piston 32 moving in the third section IN3. The hydraulic oil HF flows from one of the first and second oil chambers 31d, 31e to the other through the third communication pipe 36, not through the first and second communication pipes 34, 35. As described above, when the vibration of the rack warehouse R is relatively large so that the piston 32 is positioned in the third section IN3, the rack 32 is positioned in the first joint section IU1 including the first and second sections IN1 and IN2. The damping coefficient of the variable damping damper 6 becomes larger than the time.

  Further, when the vibration of the rack warehouse R becomes very large, the piston 32 reciprocates in the fourth section IN4 beyond the first to third sections IN1 to IN3. When the piston 32 moves toward the side opposite to the neutral position in the fourth section IN4, the check oil 45L and 45R described above causes the hydraulic oil HF to pass through the fourth communication pipes 37L and 37R. The flow from one of the two oil chambers 31d and 31e to the other is prevented.

  As is apparent from the above configuration, when the piston 32 is moving toward the side opposite to the neutral position in the fourth section IN4, the first and second oil chambers 31d and 31e are connected to the first to fourth communication pipes. When the pressure of the hydraulic oil HF in the first or second oil chamber 31d, 31e pressed by the piston 32 reaches the upper limit value without being communicated with each other via 34 to 36, 37L, 37R, The first or second relief valves 43 and 44 are opened to communicate with each other. Accordingly, the hydraulic oil HF pressed by the moving piston 32 flows from one of the first and second oil chambers 31d, 31e to the other via the first or second relief valve 43, 44. As described above, when the vibration of the rack warehouse R is very large, the damping coefficient of the variable damping damper 6 becomes very large.

  On the other hand, when the piston 32 is moving toward the neutral position side in the fourth section IN4, the check oil 45L and 45R causes the hydraulic oil HF to flow through the fourth communication pipes 37L and 37R. It is allowed to flow from one of the chambers 31d and 31e to the other.

  As described above, the damping coefficient of the variable damping damper 6 becomes larger as the moving range of the piston 32 becomes larger due to the increase in vibration of the rack warehouse R.

  Further, the transmission member 3, the support body 5 and the variable damping damper 6 are arranged between the mass body 2 and the rack warehouse R as follows. That is, as shown in FIG. 1, the transmission member 3 is disposed at both ends and the center of the mass body 2 in the horizontal direction. The support body 5 and the variable damping damper 6 are disposed between the transmission member 3 disposed at both ends of the mass body 2 in the horizontal direction and the transmission member 3 disposed at the center section, toward the center portion of the mass body 2. The support body 5, the variable damping damper 6 and the support body 5 are arranged in this order. Note that the arrangement of the transmission member 3, the support 5, and the variable damping damper 6 shown in FIG. 1 is merely an example, and it is needless to say that the arrangement is not limited thereto.

  Further, the predetermined distance DI between the abutting plate 4 and the sliding plate 21 of the support 5 is set as follows. That is, as the additional vibration system vibrates during the vibration of the rack warehouse R, the transmission member 3 that supports the mass body 2 is shown in FIG. It will be sheared and deformed. In this case, the greater the vibration of the rack warehouse R, the greater the vibration of the additional vibration system, and the greater the degree of shear deformation of the transmission member 3.

  The predetermined interval DI is when the piston 32 is located in a section composed of the second section IN2 to the fourth section IN4 because the vibration of the rack warehouse R is relatively large, that is, in a section other than the first section IN1. When positioned, the contact plate 4 and the sliding plate 21 are set to contact each other when the mass body 2 approaches the rack warehouse R due to the above-described shear deformation of the transmission member 3. In this case, the greater the degree of shear deformation of the transmission member 3 due to the relatively large vibration of the rack warehouse R, the closer the mass body 2 is to the rack warehouse R. Therefore, the contact between the contact plate 4 and the sliding plate 21 The degree is greater. Note that the mass body 2 is supported by both the transmission member 3 and the support body 5 in a state where the contact plate 4 and the sliding plate 21 of the support body 5 are in contact with each other.

  FIG. 8A shows the relationship between the horizontal deformation amount of the transmission member 3 (hereinafter referred to as “transmission member deformation amount DE”) and its resistance force (hereinafter referred to as “transmission member resistance force RE”). . FIG. 8B shows the relationship between the transmission member deformation amount DE and the frictional force between the contact plate 4 and the sliding plate 21 (hereinafter referred to as “contact friction force FR”). ) Shows the relationship between the transmission member deformation amount DE and the sum of the transmission member resistance force RE and the contact friction force FR (hereinafter referred to as “joint resistance force UR”).

  Since the transmission member 3 is made of rubber as described above, as shown in FIG. 8A, the transmission member resistance force RE increases linearly as the transmission member deformation amount DE increases. Further, the predetermined distance DI between the contact plate 4 and the sliding plate 21 is set as described above, and the larger the transmission member deformation amount DE, the more the contact degree between the both plates 4 and 21 is. As shown in FIG. 8B, the contact friction force FR becomes 0 when the transmission member deformation amount DE is relatively small, and in a range where the transmission member deformation amount DE is relatively large, as shown in FIG. The larger the value, the larger the linearity. Note that the contact friction force FR differs in the direction opposite to the transmission member resistance force RE when the transmission member deformation amount DE increases and when it decreases.

  Moreover, since the joint resistance force UR is the sum of the transmission member resistance force RE and the contact friction force FR, the relationship between the transmission member deformation amount DE and the joint resistance force UR is shown in FIGS. The relationship shown in FIG. 8C obtained by adding the relationships shown in FIG. As shown in the figure, when the transmission member deformation amount DE increases, the joint resistance force UR increases as the DE increases, due to the hysteresis characteristics shown in FIG.

  The specifications of the additional vibration system (the mass body 2, the transmission member 3, and the variable damping damper 6) are the same as those of the additional vibration system when the piston 32 is positioned in the first section IN1 during vibration of the rack warehouse R. The natural frequency is set so as to be synchronized with the natural frequency of the rack warehouse R (for example, the natural frequency of the primary mode). The setting is performed based on, for example, fixed point theory. Here, the natural frequency of the additional vibration system is determined by the mass md of the mass body 2 and the rigidity θT of the transmission member 3 (= sqrt (θT / md) / 2π). The specifications of the additional vibration system include the mass md of the mass body 2, the rigidity θT of the transmission member 3, the viscosity coefficient of the hydraulic oil HF, the cross-sectional area of the cylinder 31, and the breakage of the first to third communication pipes 34 to 36. Area and length are included.

  As described above, according to the first embodiment, the mass body 2 is supported in a mounted state on the transmission member 3 attached to the upper end of the rack warehouse R, and the cylinder of the variable damping damper 6 is supported. 31 is connected to the mass body 2 and the piston 32 is connected to the rack warehouse R. Further, an additional vibration system is configured by the mass body 2, the transmission member 3, and the variable damping damper 6, and the additional vibration system vibrates (resonates) with the vibration of the rack warehouse R, and the piston 32 moves during the vibration. Reciprocates in the cylinder 31.

  When the piston 32 is located in a predetermined first section IN1 in the cylinder 31 including the neutral position shown in FIG. 4, the first and second oil chambers 31d and 31e of the cylinder 31 are connected via the first communication pipe 34. Communicate with each other. Further, the first and second oil chambers 31d and 31e are configured so that the piston 32 is located in the first joint section IU1 including the first and second sections IN1 and IN2 in the cylinder 31, and the second communication pipe 35 is provided. When the pistons 32 are located in the second joint section IU2 including the first to third sections IN1 to IN3 in the cylinder 31, they communicate with each other via the third communication pipe 36.

  As described above, when the piston 32 is located in the first section IN1 because the vibration of the rack warehouse R is relatively small, the first and second oil chambers 31d and 31e are connected to the first to third communication pipes 34 to 34. By communicating with each other via 36, the damping coefficient of the variable damping damper 6 becomes relatively small. Further, when the vibration of the rack warehouse R is relatively large and the piston 32 is positioned in the second section IN2, the first and second oil chambers 31d and 31e are connected via the second and third communication pipes 35 and 36, respectively. Accordingly, the damping coefficient of the variable damping damper 6 becomes larger than when the piston 32 is positioned in the first section IN1. When the piston 32 is located in the third section IN3 due to the greater vibration of the rack warehouse R, the first and second oil chambers 31d and 31e communicate with each other via the third communication pipe 36, The damping coefficient of the variable damping damper 6 becomes larger than when the piston 32 is located in the second section IN2.

  The specifications of the additional vibration system are as follows: when the piston 32 is positioned in the first section IN1 during the vibration of the rack warehouse R, that is, when the vibration of the rack warehouse R is relatively small. The natural frequency is set so as to synchronize with the natural frequency of the rack warehouse R. Therefore, when the vibration of the rack warehouse R is relatively small, the vibration can be appropriately suppressed. Furthermore, when the vibration of the rack warehouse R is relatively large, a larger damping force of the mass body 2 and the variable damping damper 6 connected to the rack warehouse R can be obtained, resulting in an excessive displacement of the additional vibration system. Damage to the vibration suppressing device 1 and the rack warehouse R can be prevented. Further, unlike the above-described conventional vibration suppression device, the first to third communication pipes 34 to 36 are not relatively complicated hydraulic circuits including the first and second pressure regulating valves and the first and second spool valves. The effects described above can be obtained with a simple configuration.

  Further, a contact plate 4 is attached to the mass body 2, and a support body 5 is attached to the rack warehouse R, and the sliding plate 21 of the support body 5 has a predetermined distance DI from the contact plate 4. Opposite in state. As described above, when the rack warehouse R is not vibrating, or when the piston 32 is positioned in the first section IN1 due to the relatively small vibration of the rack warehouse R, the contact plate 4 and the sliding plate 21 are When the piston 32 is positioned in the second section IN2 to the fourth section IN4 due to the relatively large vibrations of the rack warehouse R that are not in contact with each other, the contact plate 4 and the sliding plate 21 are in contact with each other. become. Thereby, when the vibration of the rack warehouse R is relatively large, in addition to the greater damping force of the variable damping damper 6 described above, a contact friction force FR between the contact plate 4 and the sliding plate 21 is further obtained. Therefore, the above-described effect, that is, the effect of preventing the vibration suppressing device 1 and the rack warehouse R from being damaged due to excessive displacement of the additional vibration system when the vibration of the rack warehouse R is relatively large can be reliably obtained. be able to.

  The first relief valve 43 is opened when the pressure of the hydraulic oil HF in the first oil chamber 31d reaches the upper limit value, and the second relief valve 44 is opened in the hydraulic oil HF in the second oil chamber 31e. When the pressure reaches the upper limit, the valve is opened, and the first and second oil chambers 31d and 31e are communicated with each other. Furthermore, the variable damping damper 6 is provided with fourth communication pipes 37L and 37R for communicating the first and second oil chambers 31d and 31e with each other when the piston 32 is positioned in the fourth section IN4. The fourth communication pipes 37L and 37R are provided with check valves 45L and 45R. When the piston 32 is moving toward the opposite side to the neutral position in the fourth section IN4, the check valves 45L and 45R communicate with the fourth communication from one of the first and second oil chambers 31d and 31e to the other. The other of the first and second oil chambers 31d and 31e when the flow of the hydraulic oil HF through the pipes 37L and 37R is blocked and the piston 32 is moving toward the neutral position side in the fourth section IN4. The hydraulic fluid HF is allowed to flow from the first to the other through the fourth communication pipes 37L and 37R.

  As described above, when the piston 32 is moving toward the side opposite to the neutral position in the fourth section IN4 because the vibration of the rack warehouse R is very large, the first and second oil chambers 31d and 31e are When the pressure of the hydraulic oil HF in the first or second oil chamber 31d, 31e reaches the upper limit value, the first to fourth communication pipes 34 to 36, 37L, 37R are not communicated with each other. The first and second relief valves 43 and 44 are opened to communicate with each other. Accordingly, the hydraulic oil HF pressed by the moving piston 32 flows from one of the first and second oil chambers 31d, 31e to the other via the first or second relief valve 43, 44. As described above, when the vibration of the rack warehouse R is very large, a very large damping force of the variable damping damper 6 can be obtained. Therefore, the vibration suppression device 1 and the rack warehouse R caused by excessive displacement of the additional vibration system can be obtained. Breakage can be prevented.

  Further, when the piston 32 is moving toward the neutral position side in the fourth section IN4 because the vibration of the rack warehouse R is very large, the hydraulic oil HF in the other of the first and second oil chambers 31d and 31e is removed. The piston 32 can be prevented from returning to the neutral position because it can escape to one of the first and second oil chambers 31d and 31e via the fourth communication pipes 37L and 37R. In this case, since the fourth communication pipes 37L and 37R are arranged as described with reference to FIG. 6, the piston 32 is a boundary line between the third section IN3 and the fourth section IN4 (in the figure, a one-dot chain line). The fourth communication pipes 37L and 37R are not completely blocked by the piston 32 when positioned above, and the above-described effects can be obtained appropriately.

  In the first embodiment, the cross-sectional areas and lengths of the fourth communication pipes 37L and 37R are the same as the damping coefficient of the variable damping damper 6 when the piston 32 moves toward the neutral position side in the fourth section IN4. However, although it is set so that it may become the same as the damping coefficient of the variable damping damper 6 when the piston 32 is located in 3rd area IN3, of course, it is not limited to this.

  Further, since the vibration suppressing device 1 is provided at the upper end of the rack warehouse R, unlike the case where it is provided at a portion other than the upper end of the rack warehouse R, the luggage in the rack warehouse R is moved to another location. The installation work can be performed without the need.

  In the first embodiment, the cylinder 31 is connected to the mass body 2 and the piston 32 is connected to the rack warehouse R. Conversely, the cylinder 31 is connected to the rack warehouse R and the piston 32 is connected to the mass body R. 2 may be connected to each other. In the first embodiment, the cross-sectional shape of the cylinder 31, the piston 32, and the first to fourth communication pipes 34 to 36, 37L, and 37R is circular, but may be a triangle or a quadrangle. Furthermore, in 1st Embodiment, although the 1st-3rd communication pipes 34-36 are provided in parallel with each other, while the part extended in the axial direction of those cylinders is shared, and it comprises with one communication pipe, You may comprise so that it may mutually branch by the part extended in the radial direction of a cylinder, and may connect with a 1st and 2nd oil chamber (refer FIG. 12 mentioned later).

  In the first embodiment, the second and third communication pipes 35 and 36 are used as the outer communication paths in the present invention, but either one of the both 35 or 36 may be used, or each other in the cylinder. Three or more communication pipes that allow the first and second fluid chambers to communicate with each other in different sections may be used. Further, as shown in FIG. 9, an outer communication path OP in which one end portion and the other end portion thereof are respectively connected to the left wall 31 a and the right wall 31 b of the cylinder 31 may be used. Alternatively, as shown in FIG. 10, a relatively small hole V penetrating in the axial direction formed in the piston 32 may be used as the outer communication path. When the outer communication path as shown in FIGS. 9 and 10 is used, the first and second relief valves may be omitted, and the fourth communication pipes 37L and 37R are not necessary. Alternatively, the first and second relief valves may be used as the outer communication path instead of the hole V shown in FIG. 10, and in that case, it is preferable to provide the fourth communication pipes 37L and 37R.

  Furthermore, in the first embodiment, the first communication pipe 34 connected to the cylinder 31 is used as the inner communication path, but a communication path formed on the peripheral wall of the cylinder may be used. In this case, the inner communication path may be configured as a hole-shaped path that extends in the axial direction inside the peripheral wall and extends in the radial direction at both ends thereof and communicates with the first and second fluid chambers. You may comprise by the groove | channel formed in the inner peripheral surface. When the inner communication path is constituted by such a groove, the groove may be provided partially in the circumferential direction of the peripheral wall or in the entire circumferential direction. In the latter case, the rod is disposed in the axial direction of the piston. Preferably, the rods are provided so as to extend to both outer sides of the cylinders, and the rods are inserted into and supported by rod guide holes formed in the left and right walls of the cylinder. The above variations related to the inner communication path also apply to the outer communication path and the communication path. Also, when the communication passage formed on the peripheral wall of the cylinder is used as the outer communication passage, the number thereof is arbitrary.

  Moreover, in 1st Embodiment, although the hydraulic fluid HF comprised with the silicone oil is used as a working fluid in this invention, you may use the other appropriate fluid which has viscosity. Furthermore, in the first embodiment, the mass body 2 is connected to the rack warehouse R via the transmission member 3 made of laminated rubber. However, other suitable transmission members having elasticity, for example, conventional vibrations are used. The mass body may be connected to the rack warehouse like a pendulum via a wire made of a steel wire or the like in the same manner as the suppression device. In the first embodiment, the mass body 2 is connected to the upper end portion of the rack warehouse R, but may be connected to another appropriate portion.

  Furthermore, in the first embodiment, the contact plate 4 is attached to the mass body 2 and the support body 5 is attached to the rack warehouse R. Conversely, the contact plate is attached to the rack warehouse and the support body is attached to the rack warehouse R. You may attach to a mass body, respectively. Moreover, in 1st Embodiment, although the contact plate 4 attached to the mass body 2 is used as a contact body in this invention, you may use the contact body integrally provided in the mass body, Alternatively, a part of the mass body may be used as the contact body. Furthermore, in the first embodiment, the support 5 is made of laminated rubber, but may be made of another appropriate material, for example, steel. Moreover, in 1st Embodiment, although the pressure of the hydraulic fluid HF which the 1st and 2nd relief valves 43 and 44 open is set to the mutually same upper limit value, you may set to a mutually different value.

  Furthermore, although 1st Embodiment is the example which applied the vibration suppression apparatus 1 by this invention to the rack warehouse R, you may apply to another suitable structure, for example, a high-rise building. Of course, the above-described variations related to the first embodiment may be appropriately combined and employed. In addition, it is possible to appropriately change the detailed configuration within the scope of the gist of the present invention.

  Next, a vibration suppression device 51 according to a second embodiment of the present invention will be described with reference to FIGS. The vibration suppressing device 51 is for suppressing vibration of a high-rise building B standing on a foundation (not shown), and is provided between the upper and lower beams BU and BD of the building B. The vibration suppressing device 51 includes a first transmission member TM1 and a second transmission member TM2 attached to the upper and lower beams BU and BD, respectively, and a variable damping mass damper 52. 1st and 2nd transmission member TM1, TM2 is comprised with the pillar material which has elasticity, for example, H-shaped steel.

  The variable damping mass damper 52 is a combination of a mass damper and a passive type variable damping damper, and is provided in a cylindrical cylinder 53 and slidable in the axial direction in the cylinder 53 as shown in FIG. And a rod 55 which is provided integrally with the piston 54 and partially accommodated in the cylinder 53 so as to be movable in the axial direction. Hereinafter, the variable damping mass damper 52 will be described with the left side and the right side in FIG. 12 as “left” and “right”, respectively.

  Similar to the cylinder 31 described in the first embodiment, the cylinder 53 includes a left wall 53a and a right wall 53b that face each other, and a peripheral wall 53c that is integrally provided between the both 53a and 53b. The oil chamber defined by the left and right walls 53a, 53b and the peripheral wall 53c is divided into a first oil chamber 53d on the left side and a second oil chamber 53e on the right side by the piston 54, and both the oil chambers 53d, 53e. Is filled with hydraulic oil HO made of silicon oil. Further, a rod guide hole 53f penetrating in the left-right direction (axial direction) is formed at the radial center of the right wall 53b, and a seal 61 is provided in the rod guide hole 53f. Further, the left wall 53a is integrally provided with a convex portion 53g protruding leftward, and the convex portion 53g is provided with a first attachment FL1 'via a universal joint.

  The rod 55 is inserted into the rod guide hole 53f via the seal 61, extends in the axial direction, and is movable in the axial direction with respect to the cylinder 53. The left end portion of the rod 55 is attached to the piston 54. Yes. Further, a second fixture FL2 'is provided at the right end of the rod 55 via a universal joint.

  The piston 54 is formed in a columnar shape, and a seal 62 is provided on the peripheral surface thereof. When the building B is not vibrating, as shown in FIG. Located in neutral position. The neutral position is not limited to this, and may be a position on the left side or the right side of the center of the cylinder 31 in the axial direction. In addition, a plurality of holes penetrating in the axial direction are formed in the radially outer end of the piston 54 (only two are shown), and the first relief valve 63 and the second relief valve are formed in these holes. 64 is provided.

  These first and second relief valves 63 and 64 are configured similarly to the first and second relief valves 43 and 44 described in the first embodiment. The first relief valve 63 includes a valve body and a spring that biases the valve body toward the valve closing side, and the pressure of the hydraulic oil HO in the first oil chamber 53d by the movement of the piston 54 accompanying the vibration of the building B. Is opened when reaches a predetermined upper limit value. As a result, the first and second oil chambers 53d and 53e communicate with each other, thereby preventing the pressure of the hydraulic oil HO in the first oil chamber 53d from becoming excessive. The second relief valve 64 is configured by a valve body and a spring that biases the valve body toward the valve closing side, and the pressure of the hydraulic oil HO in the second oil chamber 53e by the movement of the piston 54 accompanying the vibration of the building B. Is opened when the above upper limit is reached. As a result, the first and second oil chambers 53d and 53e communicate with each other, thereby preventing the pressure of the hydraulic oil HO in the second oil chamber 53e from becoming excessive.

  The variable damping mass damper 52 further includes a first communication pipe D1, a second communication pipe D2, and third communication pipes D3L and D3R that are connected to the cylinder 53 and have a circular cross section. The cross-sectional areas of the first to third communication pipes D1, D2, D3L, D3R are set to be smaller than the cross-sectional area of the cylinder 53, and the cross-sectional areas of the first and second communication pipes D1, D2 are mutually It is set to the same value. In FIG. 11, for convenience, the first to third communication pipes D1, D2, D3L, and D3R are omitted.

  The first and second communication pipes D <b> 1 and D <b> 2 share a merge pipe DC having a circular cross section extending in parallel with the cylinder 53. The first communication pipe D1 further includes a pair of left and right communication pipes D1a and D1b. The left and right communication pipes D1a and D1b communicate with the junction pipe DC, and the inner wall surface on the neutral position side at the connection portion with the cylinder 53 includes a predetermined first section IN1 ′ including the neutral position in the cylinder 53. Are arranged so as to be flush with the left end and the right end of each. When the piston 54 is positioned in the first section IN1 ', the left communication pipe D1a communicates with the first oil chamber 53d, and the right communication pipe D1b communicates with the second oil chamber 53e. With the above configuration, when the piston 54 is positioned in the first section IN1 ′, the first communication pipe D1 including the junction pipe DC bypasses the piston 54 and connects the first and second oil chambers 53d and 53e to each other. Communicate. In the second embodiment, the center of the first section IN1 'in the axial direction coincides with the neutral position, but may be shifted.

  The second communication pipe D2 further includes a pair of left and right communication pipes D2a and D2b. The left and right communication pipes D2a and D2b communicate with the junction pipe DC, extend in parallel with the cylinder 53 from the junction pipe DC, and extend toward the cylinder 53 at their axial ends. Are arranged so that the inner wall surface on the neutral position side at the connecting portion is flush with the left end and the right end of the predetermined joint section IU in the cylinder 53. The joint section IU is composed of the first section IN1 'and a predetermined second section IN2' on both outer sides in the axial direction of the first section IN1 'in the cylinder 53.

  When the piston 54 is positioned in the joint section IU, the left communication pipe D2a communicates with the first oil chamber 53d, and the right communication pipe D2b communicates with the second oil chamber 53e. With the above configuration, when the piston 54 is positioned in the joint section IU, the second communication pipe D2 including the joining pipe DC and the left and right communication pipes D2a and D2b bypasses the piston 54, and the first and second oils The chambers 53d and 53e are communicated with each other.

  The length of the second section IN2 ′ in the axial direction is such that the communication pipes D1a and D1b of the first communication pipe D1 are blocked by the piston 54 when the piston 54 is located in the second section IN2 ′. It is preferable to set. This prevents the piston 54 located in the second section IN2 ′ from being bypassed by the communication pipe D2a (D2b) of the second communication pipe D2 and the communication pipe D1a (D1b) of the first communication pipe D1. The Alternatively, the right and left communication pipes D1a and D1b are prevented from flowing the hydraulic oil HO from the joining pipe DC side to the first and second oil chambers 53d and 53e side, and the first and second oil chambers 53d and 53e side A check valve that allows the flow of the hydraulic oil HO from the pipe to the junction pipe DC side may be provided. As a result, when the piston 54 moves to the side opposite to the neutral position in the second section IN2 ′, the hydraulic oil HO passes through the communication pipe D2a (D2b) and the communication pipe D1a (D1b). It is prevented that the oil chambers 53d and 53e flow from one to the other. In the second embodiment, the length in the axial direction of the second section IN2 'on the left side and that of the second section IN2' on the right side are the same, but may be different.

  The third communication pipes D3L and D3R are formed of a pair of left and right communication pipes, and the piston 54 is a predetermined third section on the outermost side on both outer sides in the axial direction with respect to the second section IN2 ′ in the cylinder 53. When located at IN3 ′, the piston 54 is bypassed, and the first and second oil chambers 53d and 53e are provided in communication with each other. More specifically, as shown in FIG. 13, the third communication pipe D3L on the left side has an inner wall surface on the neutral position side (right side) connected to the cylinder 53 at the end of the joint section IU. It arrange | positions so that it may become flush with the wall surface by the side of the neutral position of the piston 54 located. Further, the left third communication pipe D3L has an inner wall surface opposite to the neutral position at the connection portion on the opposite side (left side) to the neutral position of the cylinder 53 so as to be flush with the inner wall surface of the left wall 53a. Have been placed. The right third communication pipe D3R is arranged symmetrically with the left third communication pipe D3L, and the arrangement of the left third communication pipe D3L as described above is the same for the right third communication pipe D3R. It is.

  In the second embodiment, the length in the axial direction of the left third section IN3 'is the same as that of the right third section IN3', but may be different.

  Further, check valves 56L and 56R are provided on the left and right third communication pipes D3L and D3R, respectively. The left check valve 56L is configured such that the hydraulic oil HO is pressed by the piston 54 when the piston 54 moves toward the side opposite to the neutral position (left side) in the left third section IN3 ′. The flow from the first oil chamber 53d to the second oil chamber 53e through the third communication pipe D3L is prevented. Further, the check valve 56L is configured such that the hydraulic oil HO is pressed by the piston 54 when the piston 54 is moving toward the neutral position side (right side) in the left third section IN3 ′. It is allowed to flow from the second oil chamber 53e to the first oil chamber 53d through the communication pipe D3L.

  The right check valve 56R is configured such that the hydraulic oil HO is pressed by the piston 54 when the piston 54 moves toward the side opposite to the neutral position (right side) in the right third section IN3 ′. The flow from the second oil chamber 53e to the first oil chamber 53d through the third communication pipe D3R is prevented. Further, the check valve 56R is configured such that the hydraulic oil HO is pressed by the piston 54 when the piston 54 is moving toward the neutral position side (left side) in the right third section IN3 ′. It is allowed to flow from the first oil chamber 53d to the second oil chamber 53e via the communication pipe D3R.

  The variable damping mass damper 52 further includes a gear motor 71 provided in the middle of the junction pipe DC and a rotation mass 77 connected to the gear motor 71. The gear motor 71 and the rotary mass 77 are configured in the same manner as that described in FIG. 12 of Japanese Patent No. 5191579 by the present applicant. Specifically, the gear motor 71 is of a circumscribed gear type, and includes a casing 72 and a first gear 73 and a second gear 74 accommodated in the casing 72. The casing 72 is integrally provided at the center of the junction pipe DC, and the inside thereof communicates with the junction pipe DC via two entrances 72a and 72a facing each other.

  The first gear 73 is a spur gear and is provided integrally with the first rotating shaft 75. The first rotating shaft 75 extends horizontally in a direction orthogonal to the merge pipe DC, is rotatably supported by the casing 72, and slightly protrudes outside the casing 72. Similar to the first gear 73, the second gear 74 is configured by a spur gear, is provided integrally with the second rotating shaft 76, and meshes with the first gear 73. The second rotating shaft 76 extends in parallel with the first rotating shaft 75 and is rotatably supported by the casing 72. Further, the meshing portions of the first and second gears 73 and 74 face the entrances 72 a and 72 a of the casing 72.

  The rotary mass 77 is made of a material having a relatively large specific gravity, for example, a disk made of iron. The rotating mass 77 is coaxially fixed to the first rotating shaft 75 and is rotatable together with the first gear 73 and the first rotating shaft 75.

  In addition, the above-described first attachment FL1 ′ of the variable damping mass damper 52 is attached to the first transmission member TM1, and the second attachment FL2 ′ is attached to the second transmission member TM2, respectively. It extends to. As described above, the cylinder 53 of the variable damping mass damper 52 is connected to the upper beam BU and the piston 54 is connected to the lower beam BD.

  In the vibration suppressing device 51 having the above configuration, the variable damping mass damper 52 including the rotating mass 77, the first and second transmission members TM1 and TM2 constitute an additional vibration system, and the additional vibration system vibrates the building B. The vibration of the building B is absorbed and suppressed by vibrating (resonating) as it is done. Further, the piston 54 of the variable damping mass damper 52 reciprocates in the cylinder 53 as the building B vibrates. When the vibration of the building B is relatively small, the piston 54 reciprocates in the first section IN1 ′, and the hydraulic oil HO pressed by the moving piston 54 passes through the first and second communication pipes D1, D2. The fluid flows from one of the first and second oil chambers 53d and 53e to the other.

  As described above, when the vibration of the building B is relatively small, and the piston 54 is positioned in the first section IN1 ', the damping coefficient of the variable damping mass damper 52 is relatively small. When the vibration of the building B increases, the piston 54 reciprocates in the second section IN2 ′ beyond the first section IN1 ′, and is actuated by the piston 54 moving in the second section IN2 ′. The oil HO flows from one of the first and second oil chambers 53d and 53e to the other through the second communication pipe D2, not through the first communication pipe D1. As described above, when the vibration of the building B is relatively large, and the piston 54 is located in the second section IN2 ′, the damping coefficient of the variable damping mass damper 52 is larger than that in the first section IN1 ′. Becomes bigger.

  Further, when the vibration of the building B becomes very large, the piston 54 reciprocates in the third section IN3 'beyond the first and second sections IN1' and IN2 '. When the piston 54 moves toward the side opposite to the neutral position in the third section IN3 ′, the hydraulic oil HO is passed through the third communication pipes D3L and D3R by the check valves 56L and 56R described above. The flow from one of the second oil chambers 53d and 53e to the other is prevented.

  As apparent from the above configuration, when the piston 54 is moving toward the side opposite to the neutral position in the third section IN3 ′, the first and second oil chambers 53d and 53e are in communication with the first to third communication. When the pressure of the hydraulic oil HO in the first or second oil chamber 53d, 53e pressed by the piston 54 reaches the upper limit value without being communicated with each other via the pipes D1, D2, D3L, D3R The first or second relief valves 63 and 64 are opened to communicate with each other. Accordingly, the hydraulic oil HO pressed by the moving piston 54 flows from one of the first and second oil chambers 53d, 53e to the other via the first or second relief valve 63, 64. As described above, when the vibration of the building B is very large, the damping coefficient of the variable damping mass damper 52 becomes very large.

  On the other hand, when the piston 54 is moving toward the neutral position side in the third section IN3 ′, the hydraulic oil HO is fed through the third communication pipes D3L and D3R by the check valves 56L and 56R. It is allowed to flow from the other of the oil chambers 53d and 53e to one.

  As described above, the damping coefficient of the variable damping mass damper 52 becomes larger as the moving range of the piston 54 becomes larger due to the increase in the vibration of the building B.

  Further, when the hydraulic oil HO flows in the first and second communication pipes D1 and D2 or the second communication pipe D2 as described above, the inside of the joining pipe DC of the first and second communication pipes D1 and D2 The flow of the hydraulic oil HO is transmitted to the rotary mass 77 in a state converted into a rotary motion by the gear motor 71, whereby the rotary mass 77 rotates.

  The specifications of the additional vibration system (the variable damping mass damper 52, the first and second transmission members TM1, TM2) are the additional vibration system when the piston 54 is positioned in the first section IN1 ′ during the vibration of the building B. Is set so as to synchronize with the natural frequency of the building B (for example, the natural frequency of the primary mode). The setting is performed based on, for example, fixed point theory. Here, the natural frequency of the additional vibration system is determined by the mass of the rotating mass 77 and the rigidity of the first and second transmission members TM1 and TM2, as in the first embodiment. The specifications of the additional vibration system include the mass of the rotating mass 77, the rigidity of the first and second transmission members TM1 and TM2, the viscosity coefficient of the hydraulic oil HO, the cross-sectional area of the cylinder 53, and the first and second The cross-sectional areas and lengths of the communication pipes D1 and D2 are included.

  As described above, according to the second embodiment, the cylinder 53 and the piston 54 of the variable damping mass damper 52 are respectively connected to the upper beam BU and the lower beam BD of the building B via the first and second transmission members TM1 and TM2. It is connected to. Further, an additional vibration system is constituted by the variable damping mass damper 52 and the first and second transmission members TM1 and TM2, and the additional vibration system vibrates (resonates) with the vibration of the building B. During vibration of the building B, the relative displacement between the upper beam BU and the lower beam BD is transmitted to the piston 54 and the cylinder 53, whereby the piston 54 reciprocates in the cylinder 53.

  When the piston 54 is positioned in a predetermined first section IN1 ′ in the cylinder 53 including the neutral position shown in FIG. 12, the first and second oil chambers 53d and 53e of the cylinder 53 are connected to the first communication pipe D1. Are communicated with each other. The first and second oil chambers 53d and 53e are configured so that the piston 54 is located in the joint section IU including the first and second sections IN1 ′ and IN2 ′ in the cylinder 53. Are communicated with each other.

  As described above, when the vibration of the building B is relatively small and the piston 54 is positioned in the first section IN1 ′, the first and second oil chambers 53d and 53e are connected to the first and second communication pipes D1, By communicating with each other via D2, the damping coefficient of the variable damping mass damper 52 becomes relatively small. When the vibration of the building B is relatively large and the piston 54 is located in the second section IN2 ′, the first and second oil chambers 53d and 53e are communicated with each other via the second communication pipe D2. Thus, the damping coefficient of the variable damping mass damper 52 becomes larger than when the piston 54 is positioned in the first section IN1 ′.

  In addition, during the vibration of the building B, the hydraulic oil HO pressed by the piston 54 moving in the cylinder 53 flows through the merge pipe DC of the first and second communication pipes D1 and D2, and the flow of the hydraulic oil HO is Then, it is transmitted to the rotary mass 77 in a state converted into rotational motion by the gear motor 71, whereby the rotary mass 77 rotates. As described above, the relative displacement between the upper beam BU and the lower beam BD is transmitted to the gear motor 71 via the first and second transmission members TM1, TM2, the cylinder 53, the piston 54, and the hydraulic oil HO. The relative displacement between the upper beam BU and the lower beam BD transmitted to the gear motor 71 is transmitted to the rotating mass 77 in a state converted into a rotational motion.

  Further, the specifications of the additional vibration system are such that when the piston 54 is located in the first section IN1 ′ during the vibration of the building B, that is, when the vibration of the building B is relatively small, The frequency is set so as to synchronize with the natural frequency of the building B. Therefore, when the vibration of the building B is relatively small, the vibration can be appropriately suppressed. In this case, the effect of suppressing the vibration of the building B by the additional vibration system is enhanced by obtaining the rotation inertial mass effect by the rotation mass 77. Further, when the vibration of the building B is relatively large, a larger damping force of the variable damping mass damper 52 connected to the upper beam BU and the lower beam BD can be obtained, so that vibration caused by excessive displacement of the additional vibration system Damage to the suppression device 51 and the building B can be prevented. Further, unlike the above-described conventional vibration suppression device, it is not a complicated hydraulic circuit composed of the first and second pressure regulating valves and the first and second spool valves, but rather the first and second communication pipes D1 and D2. The effects described above can be obtained with a simple configuration.

  Further, since the mass damper and the variable damping damper are not separately configured (see FIG. 14 to be described later), but the variable damping mass damper 52 configured integrally with each other is used, the vibration suppression device 51 as a whole is reduced in size. be able to.

  The first relief valve 63 opens when the pressure of the hydraulic oil HO in the first oil chamber 53d reaches the upper limit value, and the second relief valve 64 opens the hydraulic oil HO in the second oil chamber 53e. When the pressure reaches the upper limit value, the first and second oil chambers 53d and 53e communicate with each other. Further, the variable damping mass damper 52 is provided with third communication pipes D3L and D3R for communicating the first and second oil chambers 53d and 53e with each other when the piston 54 is positioned in the third section IN3 ′. The third communication pipes D3L and D3R are provided with check valves 56L and 56R. When the piston 54 is moving toward the opposite side to the neutral position in the third section IN3 ′, the check valves 56L and 56R are the third ones from the first and second oil chambers 53d and 53e to the other. The first and second oil chambers 53d, 53e are prevented when the hydraulic oil HO is prevented from flowing through the communication pipes 56L, 56R and the piston 54 is moving toward the neutral position side in the third section IN3 ′. The hydraulic fluid HO is allowed to flow through the third communication pipes 56L and 56R from the other side to the other side.

  As described above, when the piston 54 is moving toward the side opposite to the neutral position in the third section IN3 ′ because the vibration of the building B is very large, the first and second oil chambers 53d and 53e are When the pressure of the hydraulic oil HO in the first or second oil chamber 53d, 53e reaches the upper limit value without being communicated with each other via the first and second communication pipes D1, D2, the first or second The relief valves 63 and 64 are opened to communicate with each other. Accordingly, the hydraulic oil HO pressed by the moving piston 54 flows from one of the first and second oil chambers 53d, 53e to the other via the first or second relief valve 63, 64. As described above, when the vibration of the building B is very large, a very large damping force of the variable damping mass damper 52 can be obtained. Therefore, the vibration suppressing device 51 and the building B caused by excessive displacement of the additional vibration system can be prevented. Can be prevented.

  Further, when the piston 54 is moving toward the neutral position side in the third section IN3 ′ because the vibration of the building B is very large, the hydraulic oil HO in the other of the first and second oil chambers 53d and 53e is removed. The piston 54 can be prevented from returning to the neutral position because it can escape to one of the first and second oil chambers 53d and 53e via the third communication pipes D3L and D3R. In this case, since the third communication pipes D3L and D3R are arranged as described with reference to FIG. 13, the piston 54 has a boundary line between the second section IN2 ′ and the third section IN3 ′ (one point in FIG. The third communication pipes D3L and D3R are not completely blocked by the piston 54 when positioned above (illustrated by chain lines), and the above-described effects can be appropriately obtained.

  In the second embodiment, the cross-sectional areas and lengths of the third communication pipes D3L and D3R are the same as the damping of the variable damping mass damper 52 when the piston 54 moves toward the neutral position side in the third section IN3 ′. The coefficient is set so as to be the same as the damping coefficient of the variable damping mass damper 52 when the piston 54 is positioned in the second section IN2 ′, but it is of course not limited thereto.

  In the second embodiment, the variable damping mass damper 52 in which the mass damper and the variable damping damper are integrally formed is used. However, as shown in FIG. 14, the mass damper 81 and the variable damping damper 82 are configured separately from each other. The both beams 81 and 82 may be connected to the upper beam BU and the lower beam BD in parallel with each other. The mass damper 81 is configured in the same manner as the mass damper disclosed in Japanese Patent No. 5314201 by the present applicant, and has a rotating mass (not shown). Further, the variable damping damper 82 differs from the variable damping mass damper 52 according to the second embodiment only in that the gear motor and the rotation mass are not provided, and the first to third communication of the variable damping damper 82 is different. Other components such as a tube (not shown) are configured in the same manner as those of the variable damping mass damper 52. Incidentally, instead of the variable damping damper 82, the variable damping damper 6 according to the first embodiment (including the modified examples shown in FIGS. 9 and 10) may be used. In this case as well, the outer communication path in the present invention is used. As an alternative, the first and second relief valves 63 and 64 may be used. Further, the mass damper 81 may be provided in parallel with the variable damping mass damper 52.

  Further, in the second embodiment, the cylinder 53 is connected to the upper beam BU and the piston 54 is connected to the lower beam BD. Conversely, the cylinder 53 is connected to the lower beam BD and the piston 54 is connected to the upper beam. You may connect with BU, respectively. In the second embodiment, the cross-sectional shapes of the cylinder 53, the piston 54, and the first to third communication pipes D1, D2, D3L, and D3R are circular, but may be a triangle or a quadrangle. Further, in the second embodiment, the gear motor 71 is provided in the junction pipe DC shared by the first and second communication pipes D1 and D2, but the entire first communication pipe and the entire second communication pipe are separated from each other. Both may be provided and connected to the gear motor 71.

  In the second embodiment, the left and right communication pipes D2a and D2b of the second communication pipe D2 are connected to the peripheral wall 53c of the cylinder 53. As shown in FIG. You may connect to the wall 53b, respectively. In this case, the first and second relief valves may be omitted, and the third communication pipes D3L and D3R are unnecessary. Further, in the second embodiment, the second communication pipe D2 is used as the outer communication path in the present invention. However, a plurality of communication pipes that connect the first and second fluid chambers to each other in different sections in the cylinder are provided. It may be used.

  Further, in the second embodiment, the first communication pipe D1 connected to the cylinder 53 is used as the inner communication path, but a communication path formed on the peripheral wall of the cylinder may be used. In this case, when using the variable damping mass damper in which the mass damper and the variable damping damper are integrated with each other, the inner communication path extends in the axial direction inside the peripheral wall, and extends in the radial direction at both ends thereof. You may comprise by the hole-shaped channel | path connected to a fluid chamber.

  Further, as shown in FIG. 14, when the mass damper 81 and the variable damping damper 82 are provided in parallel to each other, the inner communication path may be configured by the above-described hole-shaped path, or may be formed on the inner peripheral surface of the peripheral wall. You may comprise by a groove | channel. When the inner communication path is constituted by such a groove, the groove may be provided partially in the circumferential direction of the peripheral wall or in the entire circumferential direction. In the latter case, the rod is disposed in the axial direction of the piston. Preferably, the rods are provided so as to extend to both outer sides of the cylinders, and the rods are inserted into and supported by rod guide holes formed in the left and right walls of the cylinder. The above variations related to the inner communication path also apply to the outer communication path and the communication path. Also, when the communication passage formed on the peripheral wall of the cylinder is used as the outer communication passage, the number thereof is arbitrary.

  Moreover, in 2nd Embodiment, although the hydraulic fluid HO comprised by the silicone oil is used as a working fluid in this invention, you may use the other appropriate fluid which has viscosity. Furthermore, in 1st Embodiment, although 1st and 2nd transmission member TM1, TM2 is comprised with the H-shaped steel, you may comprise with another suitable material which has elasticity, for example, rubber | gum. In the second embodiment, the cylinder 53 is connected to the upper beam BU via the first transmission member TM1, and the piston 54 is connected to the lower beam BD via the second transmission member TM2. One of the cylinder and the piston is directly connected to one of the upper beam and the lower beam to which the one is connected without a transmission member, and the other of the cylinder and the piston is connected to the upper beam and the lower beam to which the other is connected. You may connect with the other side of a beam via a transmission member. Furthermore, in 2nd Embodiment, although the pressure of the hydraulic fluid HO which the 1st and 2nd relief valves 63 and 64 open is set to the mutually same upper limit value, you may set to a mutually different value.

  In the second embodiment, the external gear type gear motor 71 is used as the power conversion mechanism in the present invention. However, an internal gear type gear motor may be used, and the flow of the working fluid is further rotated. Other suitable mechanisms that transmit to the rotating mass in a state converted to motion may be used. For example, the screw mechanism described in FIG. 5 of Japanese Patent No. 5191579 by the present applicant, the ball screw in which the piston described in FIG. 2 of Japanese Patent No. 5161395 by the present applicant is integrally provided on the nut, Alternatively, a vane motor or the like may be used. When this ball screw is used as the power conversion mechanism, it is needless to say that the portion in which the piston moves in the inner communication path and the outer communication path may be formed in a cylinder shape. Further, in the second embodiment, the rod 55 is directly connected to the piston 54. However, as described in FIG. 2 of Japanese Patent No. 5191579 by the present applicant, the rod 55 is connected via a disc spring. Also good. In this case, the first fixture provided at one end of the cylinder and the second fixture provided at one end of the rod are directly connected to the upper beam and the lower beam without passing through the first and second transmission members, respectively. It may be connected in a brace shape. Alternatively, as described in, for example, FIG. 2 of Japanese Patent Application No. 2014-197837 by the present applicant, the rod may be connected to the piston via a cable, a fixed pulley, and a moving pulley. In the second embodiment, the piston 54 is connected to the lower beam BD through the rod 55. As described in FIG. 2 of Japanese Patent Application No. 2014-183201 by the applicant, It may be connected via a fixed pulley and a moving pulley.

  Further, in the second embodiment, the first and second portions in the present invention are the upper beam and the lower beam, respectively, but the foundation on which the building B is erected and other appropriate predetermined in the system including the building B These two parts, for example, the foundation and the upper end of the building may be used. The second embodiment is an example in which the vibration suppressing device 51 according to the present invention is applied to a building B, but may be applied to other appropriate structures such as a rack warehouse. Of course, the above-described variations related to the second embodiment may be appropriately combined and employed. In addition, it is possible to appropriately change the detailed configuration within the scope of the gist of the present invention.

  Next, a vibration suppressing device 91 according to a third embodiment of the present invention will be described with reference to FIGS. As shown in FIGS. 16-19, this vibration suppression apparatus 91 is compared with 1st Embodiment, The operation | movement of the flat jack 92 provided between the support body 5 and the rack warehouse R, and the flat jack 92 is carried out. The main difference is that a control device 101 for controlling is provided. 16 to 18, the same components as those in the first embodiment are denoted by the same reference numerals. Hereinafter, a description will be given focusing on differences from the first embodiment. In FIG. 16, the reference numerals of the detailed components are omitted for convenience as in FIG. 1.

  As shown in FIGS. 17 and 18, the flat jack 92 integrally includes a pair of upper and lower disk-shaped pressing plates 93, 93 and a hollow elastic portion 94 provided between the pressing plates 93, 93. It can be expanded and contracted in the vertical direction. The stretchable part 94 is composed of a pair of upper and lower relatively thin steel plates joined together, and a fluid chamber 94a capable of supplying fluid pressure (for example, hydraulic pressure) is defined inside thereof. The stretchable portion 94 has an inner peripheral portion formed in a disc shape, an outer peripheral portion formed in a ring shape, and is disposed concentrically with the press plates 93 and 93 as a whole. 93 and 93 project outward in the radial direction.

  A rectangular plate-like upper flange 95 is integrally provided on the upper surface of the upper pressing plate 93, and a rectangular plate-like lower flange 96 is provided concentrically on the bottom surface of the lower pressing plate 93. The upper flange 95 is screwed with the bolt inserted into the mounting hole 22a of the flange 22 of the support body 5 in a state in which the support body 5 described above is placed. Is attached to the upper flange 95 of the flat jack 92.

  Further, each of the four corners of the lower flange 96 is formed with a mounting hole (not shown) penetrating in the vertical direction. Bolts (not shown) are inserted into the mounting holes of the lower flange 96, and these bolts are screwed into the upper end portion of the rack warehouse R, whereby the lower flange 96 of the flat jack 92 is attached to the rack. It is attached to the upper end of the warehouse R. With the above configuration, the support 5 is provided in the rack warehouse R via the flat jack 92 so that it cannot move in the horizontal direction and can move in the vertical direction.

  Further, as shown in FIG. 17, as in the first embodiment, the sliding plate 21 of the support 5 faces the contact plate 4 of the mass body 2 with a space in the vertical direction. This interval is set to a value slightly larger than the interval DI. Furthermore, the expansion / contraction part 94 is connected to a pump and a drain (both not shown) via an injection pipe and a discharge pipe communicating with the fluid chamber 94a, respectively. In the middle of the injection pipe and the discharge pipe, a first control valve 97 and a second control valve 98 configured by, for example, linear solenoid valves are provided (see FIG. 19).

  In the flat jack 92, when the first control valve 97 is in the open state, fluid pressure from the pump is supplied to the expansion / contraction part 94, and when the first control valve 97 is in the closed state, the pump moves from the pump to the expansion / contraction part 94. The supply of the fluid pressure is stopped. When the second control valve 98 is in the open state, the fluid pressure in the expansion / contraction part 94 is discharged to the drain, and when the second control valve 98 is in the closed state, the fluid pressure from the expansion / contraction part 94 to the drain. Is stopped.

  In the flat jack 92, a jack-up mode and a jack-down mode are set as control modes of the first and second control valves 97 and 98. In the jack-up mode, the first control valve 97 is opened and the second control valve 98 is fully closed, so that the fluid pressure from the pump is supplied to the expansion / contraction part 94 and the expansion / contraction part 94 The discharge of fluid pressure to the drain is stopped. As a result, as shown in FIG. 18, as a result of the expansion / contraction part 94 swelling in the vertical direction, the distance between the upper and lower flanges 95 and 96 is increased, and the flat jack 92 is extended (jacking up). Further, the support 5 is pushed up by the extension of the flat jack 92 and pressed toward the contact plate 4 side. In this case, the fluid pressure supplied from the pump to the expansion / contraction part 94 increases as the opening degree of the first control valve 97 increases, and thereby the extension amount of the flat jack 92 increases.

  In the jackdown mode, the first control valve 97 is fully closed and the second control valve 98 is fully opened, so that the supply of fluid pressure from the pump to the expansion / contraction section 94 is stopped and the expansion / contraction section Fluid pressure is discharged from 94 to the drain. As a result, as shown in FIG. 17, as a result of the expansion / contraction part 94 contracting in the vertical direction, the distance between the upper and lower flanges 95, 96 is reduced, and the flat jack 92 is shortened (jack down).

  The first and second control valves 97 and 98 are connected to the control device 101, and the opening degrees of both the 97 and 98 are controlled by the control device 101. The control device 101 is configured by a combination of a battery, an electric circuit, a CPU, a RAM, a ROM, an I / O interface, and the like, and is provided in a building (not shown) together with the rack warehouse R.

  The mass body 2 is provided with a displacement sensor 102. The displacement sensor 102 is of a laser type, for example, detects a horizontal displacement (hereinafter referred to as “mass body displacement”) DISM of the mass body 2 with respect to the rack warehouse R, and outputs a detection signal to the control device 101. The control device 101 controls the opening degree of the first and second control valves 97 and 98 based on the detected mass displacement DISM during the vibration of the rack warehouse R, thereby controlling the flat jack 92.

  FIG. 20 shows a process executed by the control device 101 to control the flat jack 92. This process is repeatedly executed every predetermined time (for example, 10 msec). First, in step 1 of FIG. 20 (illustrated as “S1”, the same applies hereinafter), it is determined whether or not the detected mass displacement DISM is equal to or greater than the first predetermined displacement DREM1. The first predetermined displacement DREM1 is set to a value larger than ½ of the first section IN1 and less than or equal to ½ of the first or second joint section IU1, IU2.

  When the answer to step 1 is NO (DISM <DREM1), the first and second control valves 97 and 98 are controlled in the jack-down mode (step 2), and this process is terminated. Accordingly, as described above, the flat jack 92 is shortened by controlling the first and second control valves 97 and 98 to the fully closed state and the fully open state, respectively.

  On the other hand, when the answer to step 1 is YES and the mass body displacement DISM of the mass body 2 displaced by the vibration of the rack warehouse R is equal to or greater than the first predetermined displacement DREM1, the first and second control valves 97 and 98 are jacked up. Control is performed in the mode (step 3), and this process is terminated. Accordingly, as described above, the flat jack 92 is extended by controlling the first and second control valves 97 and 98 to the open state and the fully closed state, respectively.

  Further, when the mass body displacement DISM is equal to or larger than the first predetermined displacement DREM1 and smaller than the second predetermined displacement DREM2 (> DREM1) during execution of the jack-up mode in step 3, the opening degree of the first control valve 97 is set to a predetermined value. The first opening is controlled. The first opening is set to a value such that the sliding plate 21 of the support 5 comes into contact with the contact plate 4 by the extension of the flat jack 92. As described above, the support plate 5 is pressed toward the contact plate 4 by the flat jack 92, so that the sliding plate 21 contacts the contact plate 4. The second predetermined displacement DREM2 is set to a value larger than ½ of the first or second joint section IU1, IU2.

  Furthermore, when the mass body displacement DISM is equal to or greater than the second predetermined displacement DREM2 during execution of the jack-up mode in step 3, the opening degree of the first control valve 97 is a predetermined second opening degree that is larger than the first opening degree. Controlled. As a result, the extension amount of the flat jack 92 becomes larger, and the pressing force of the sliding plate 21 toward the contact plate 4 by the flat jack 92 becomes larger. As described above, during execution of the jack-up mode in step 3, the larger the mass displacement DISM, the higher the pressing force of the sliding plate 21 toward the contact plate 4 by the flat jack 92 becomes stepwise. Controlled. In this case, the number of stages is one, but a plurality of stages may be used.

  As described above, according to the third embodiment, the mass body 2 is supported in a state of being placed on the transmission member 3 attached to the rack warehouse R, and the mass body 2 includes a contact plate. 4 is integrally provided, and in the rack warehouse R, the support body 5 is provided via a flat jack 92 so as not to move in the horizontal direction and to be movable in the vertical direction. The support 5 is opposed to the contact plate 4 with a space in the vertical direction, and the support 5 is pressed toward the contact plate 4 by the flat jack 92. Further, when the mass body displacement DISM, which is the horizontal displacement of the mass body 2 with respect to the rack warehouse R due to vibration, is detected by the displacement sensor 102, and the detected mass body displacement DISM is smaller than the first predetermined displacement DREM1 (FIG. 20 Step 1: NO), the first and second control valves 97 and 98 are controlled by the control device 101 in the jack-down mode (Step 2). As a result, when the rack warehouse R is not vibrating or when the rack warehouse R has a relatively small vibration and the mass body displacement DISM is small, the sliding plate 21 of the support 5 is brought into contact with the flat jack 92. It is not pressed to the 4 side and is held so as not to contact the contact plate 4 (see FIG. 17).

  On the other hand, when the mass body 2 is displaced horizontally with respect to the rack warehouse R by the vibration of the rack warehouse R and the mass body displacement DISM reaches the first predetermined displacement DREM1 (step 1: YES), the first and second By controlling the second control valves 97 and 98 in the jack-up mode, the flat jack 92 is controlled so that the sliding plate 21 of the support 5 is brought into contact with the contact plate 4 (step 3). Then, the sliding plate 21 comes into contact with the contact plate 4 (see FIG. 18). Thereby, when the vibration of the rack warehouse R is relatively large, in addition to the greater damping force of the variable damping damper 6 described in the description of the first embodiment, the resistance due to the friction between the contact plate 4 and the sliding plate 21 is increased. More power is gained. Therefore, the effect of the first embodiment, that is, the damage of the vibration suppressing device 91 and the rack warehouse R due to the excessive displacement of the additional vibration system (displacement of the mass body) when the vibration of the rack warehouse R is relatively large. The effect of being able to prevent can be acquired reliably.

  Further, during execution of the jack-up mode, the pressing force of the sliding plate 21 toward the contact plate 4 by the flat jack 92 is controlled to be larger as the mass displacement DISM is larger. Thus, when the mass body displacement DISM is equal to or greater than the first predetermined displacement DREM1 due to the relatively large vibration of the rack warehouse R, the larger the mass body displacement DISM, the greater the friction between the contact plate 4 and the sliding plate 21. Therefore, when the vibration of the rack warehouse R is relatively large, the vibration suppressing device 91 and the rack warehouse R can be prevented from being damaged due to excessive displacement of the additional vibration system. Can be obtained more effectively.

  Further, when the transmission member 3 is replaced, the replacement is easily performed in a state where the mass body 2 is supported by the support body 5 by bringing the sliding material 21 into contact with the contact plate 4 by extending the flat jack 92. be able to. In addition, according to the third embodiment, the effects of the first embodiment can be obtained similarly.

  In the third embodiment, the contact plate 4 is provided in the mass body 2 and the support body 5 is provided in the rack warehouse R. Conversely, the contact plate is provided in the rack warehouse and the support body is provided. You may provide in a mass body, respectively. Further, in the third embodiment, the vibration suppressing device 91 is configured to press the support 5 against the contact plate 4 by the flat jack 92, but on the contrary, the contact plate is reversed. You may comprise so that 4 may be pressed and contacted to the support body 5. FIG. Furthermore, in 3rd Embodiment, although the flat jack 92 is used as a press mechanism in this invention, other suitable mechanisms which can press a contact body to the to-be-contacted body side, for example, a piston-type jack, A gear-type jack or the like may be used.

  In the third embodiment, the displacement sensor 102 is a laser type, but an ultrasonic type may also be used. Furthermore, in the third embodiment, the mass body displacement DISM is detected by the displacement sensor 102, but the relative velocity of the mass body with respect to the structure is detected by an ultrasonic sensor or the like, and the detected relative velocity is also detected. You may calculate by integrating. In the third embodiment, the mass body displacement DISM is detected as the displacement parameter in the present invention. However, other suitable parameters representing the displacement of the mass body with respect to the structure, for example, the cylinder 31 of the variable damping damper 6 are used. The displacement of the piston 32 with respect to may be detected.

  Furthermore, in the third embodiment, in the jack-up mode, the pressing force of the flat jack 92 is controlled to increase stepwise as the mass displacement DISM increases, but continuously (for example, linearly). You may control so that it may become larger. Of course, with respect to the third embodiment, the variations related to the first embodiment described above may be adopted. In addition, it is possible to appropriately change the detailed configuration within the scope of the gist of the present invention.

R rack warehouse (structure)
DESCRIPTION OF SYMBOLS 1 Vibration suppression apparatus 2 Mass body 3 Transmission member 4 Contact plate (contacted body)
5 Support body (contact body)
6 Variable damping damper 31 Cylinder 31d First oil chamber (first fluid chamber)
31e Second oil chamber (second fluid chamber)
32 piston 34 first communication pipe (inner communication path)
35 Second communication pipe (outer communication path)
36 Third communication pipe (outer communication path)
37L 4th communication pipe (communication path)
37R Fourth communication pipe (communication path)
43 1st relief valve 44 2nd relief valve 45L Check valve 45R Check valve HF Hydraulic oil (working fluid)
IN1 1st section (inner section)
IN2 Second section (first outer section)
IN3 3rd section (1st outside section)
IN4 4th section (2nd outer section)
IU1 first joint section (predetermined section)
IU2 second joint section (predetermined section)
DI Predetermined distance OP Outer communication path V Hole (outer communication path)
51 Vibration suppression device B Building (structure)
BU upper beam (first part)
BD Lower beam (second part)
TM1 first transmission member (transmission member)
TM2 Second transmission member (transmission member)
52 Variable damping mass damper (variable damping damper)
53 Cylinder 53d First oil chamber (first fluid chamber)
53e Second oil chamber (second fluid chamber)
54 Piston D1 1st communication pipe (inner communication path)
D2 Second communication pipe (outer communication path)
D3L 3rd communication pipe (communication path)
D3R 3rd communication pipe (communication path)
56L check valve 56R check valve 63 first relief valve 64 second relief valve 71 gear motor (power conversion mechanism)
77 Rotating mass HO Hydraulic oil (working fluid)
IN1 '1st section (inner section)
IN2 'second section (first outer section)
IN3 '3rd section (2nd outside section)
IU joint section (predetermined section)
82 Variable Damping Damper 91 Vibration Suppressing Device 92 Flat Jack (Pressing Mechanism)
101 Control device (control means)
102 Displacement sensor (displacement parameter detection means)
DISM mass displacement (displacement parameter)
DREM1 first predetermined displacement (predetermined displacement)

Claims (6)

A vibration suppressing device for a structure for suppressing vibration of the structure,
A mass body connected to the structure via a transmission member having elasticity;
A variable damping damper, and
The variable damping damper is
A cylinder connected to one of the structure and the mass body;
It is provided in the cylinder so as to be movable in the axial direction, divides the inside of the cylinder into a first fluid chamber and a second fluid chamber, is connected to the other of the structure and the mass body, and the structure vibrates. A piston located in a predetermined neutral position when not
A working fluid filled in the first and second fluid chambers;
An inner communication passage that bypasses the piston and communicates the first and second fluid chambers when the piston is located in a predetermined inner section including the neutral position; and
When the piston is located in a predetermined section including the inner section and a predetermined first outer section on both outer sides in the axial direction than the inner section in the cylinder, the first and second fluids An outer communication path for communicating the chambers with each other;
When the piston is located in the first outer section, the damping coefficient is configured to be larger than when the piston is located in the inner section,
The mass body, the transmission member, and the variable damping damper constitute an additional vibration system, and the specifications of the additional vibration system are such that the piston is positioned in the inner section during vibration of the structure. In some cases, the vibration suppression device for a structure is set so that the natural frequency of the additional vibration system is synchronized with the natural frequency of the structure. The transmission member is attached to the structure, and the mass body is supported in a state of being placed on the transmission member,
A contacted body integrally provided on one of the mass body and the structure;
The other of the mass body and the structure is provided so as to be immovable in the horizontal direction and movable in the vertical direction, and a contact body facing the contacted body with a space in the vertical direction,
A pressing mechanism for pressing the contact body toward the contacted body;
A displacement parameter detecting means for detecting a displacement parameter representing a horizontal displacement of the mass body relative to the structure due to vibration;
During the vibration of the structure, when the displacement of the mass body represented by the detected displacement parameter reaches a predetermined displacement, the pressing body is brought into contact with the contacted body. The structure vibration suppressing device according to claim 1, further comprising a control unit that controls the mechanism. A structure vibration suppressing device for suppressing vibration of a structure standing on a foundation,
A rotatable mass,
The relative displacement between the predetermined first part and the second part in the system including the foundation and the structure is transmitted through an elastic transmission member, and the transmitted first and second parts are transmitted. A power conversion mechanism that performs a power conversion transmission operation that transmits the relative displacement between the parts to the rotary mass in a state where the relative displacement is converted into a rotary motion;
A variable damping damper, and
The variable damping damper is
A cylinder coupled to the first portion;
It is provided in the cylinder so as to be movable in the axial direction, divides the inside of the cylinder into a first fluid chamber and a second fluid chamber, is connected to the second portion, and the structure is not vibrating. A piston located in a predetermined neutral position;
A working fluid filled in the first and second fluid chambers;
An inner communication passage that bypasses the piston and communicates the first and second fluid chambers when the piston is located in a predetermined inner section including the neutral position; and
When the piston is located in a predetermined section including the inner section and a predetermined first outer section on both outer sides in the axial direction than the inner section in the cylinder, the first and second fluids An outer communication path for communicating the chambers with each other;
When the piston is located in the first outer section, the damping coefficient is configured to be larger than when the piston is located in the inner section,
The rotating mass, the transmission member, and the variable damping damper constitute an additional vibration system, and the specifications of the additional vibration system are such that the piston is positioned in the inner section during the vibration of the structure. In some cases, the vibration suppression device for a structure is set so that the natural frequency of the additional vibration system is synchronized with the natural frequency of the structure. At least one of the cylinder and the piston is connected to at least one of the first and second parts to which the at least one is connected via the transmission member,
The power conversion mechanism transmits the relative displacement between the first and second parts via the transmission member, the cylinder, the piston and the working fluid, and performs the power conversion transmission operation. The structure vibration suppressing device according to claim 3, wherein the flow of the working fluid in the inner communication path and the outer communication path is transmitted to the rotary mass in a state of being converted into a rotational motion. The piston is opened when the pressure of the working fluid in the first fluid chamber reaches a first predetermined pressure, and a first relief valve for communicating the first and second fluid chambers with each other, and the second A second relief valve is provided that opens when the pressure of the working fluid in the fluid chamber reaches a second predetermined pressure, and causes the first and second fluid chambers to communicate with each other;
When the piston is located in a predetermined second outer section on both outer sides in the axial direction than the first outer section in the cylinder, the piston is bypassed, and the first and second fluid chambers are bypassed. A communication path for communicating with each other;
The working fluid is provided in the communication passage, and when the piston moves toward the side opposite to the neutral position in the second outer section, the working fluid passes through the communication passage and passes through the first and second fluid chambers. While preventing the flow from one side to the other, and when the piston is moving toward the neutral position side in the second outer section, the working fluid passes through the communication path and the first and second fluids. The structure vibration suppressing device according to any one of claims 1 to 4, further comprising a check valve that allows the fluid chamber to flow from the other side to the one side.   When the displacement of the mass body represented by the displacement parameter is greater than or equal to the predetermined displacement during vibration of the structure, the control means increases the pressing force of the pressing mechanism as the displacement of the mass body increases. The vibration suppression device for a structure according to claim 2, wherein the vibration suppression device is controlled to be larger.

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