JP6495795B2 - Mass damper - Google Patents

Description

  The present invention relates to a mass damper that is provided between a first part and a second part in a system including a structure and that suppresses vibration of the structure.

  Conventionally, as this type of mass damper, for example, one disclosed in Patent Document 1 is known. The mass damper includes a cylindrical outer cylinder, an end cylinder accommodated at one end in the axial direction of the outer cylinder, movably accommodated in the axial direction, and extends in the axial direction to the outer cylinder and the end cylinder in the axial direction. A screw shaft movably accommodated in the screw shaft, a disc spring unit housed in the end cylinder, and screwed to the screw shaft via a ball, and rotated to the exterior cylinder via a bearing A nut that can be accommodated, and a rotating mass that is rotatably accommodated in the outer cylinder integrally with the nut.

  Four keys extending in the axial direction are engaged with the outer cylinder and the end cylinder, thereby preventing relative rotation therebetween. The disc spring unit is composed of a plurality of disc springs stacked in the axial direction, and the end cylinder side portions of the screw shaft are respectively arranged on both sides of the disc spring unit and the disc spring unit in the axial direction. It is inserted into a pair of donut plate-like push plates. In addition, a pair of stoppers that come into contact with the pair of pressing plates from the outside are provided integrally with the end cylinder side portion of the screw shaft. Further, a pair of ring-shaped lid portions that are in contact with the pair of push plates from the outside are attached to the end cylinder. Further, an anti-rotation plate is integrally provided between the nut and the stopper of the screw shaft, and a key extending in the axial direction is engaged with the anti-rotation plate and the exterior cylinder. The rotation of the screw shaft is prevented.

  In the conventional mass damper having the above-described configuration, the exterior cylinder and the end cylinder are respectively connected to the predetermined first part and the second part of the structure, and the first part and the second part associated with the vibration of the structure are provided. The relative displacement between them is transmitted to the outer cylinder and the end cylinder. Along with this, when the end cylinder moves to the nut side relative to the exterior cylinder due to the compressive force acting on the mass damper, one lid of the end cylinder presses one push plate toward the nut side, As a result, one push plate moves away from one stopper, and the movement of the end cylinder relative to the exterior cylinder is transmitted to the screw shaft via the one push plate, the disc spring unit, the other push plate, and the other stopper. . Thereby, a nut and a rotation mass rotate in one as a screw axis moves to the nut side.

  On the other hand, when the end cylinder moves to the opposite side of the nut relative to the exterior cylinder due to the tensile force acting on the mass damper, the other lid of the end cylinder presses the other push plate to the opposite side of the nut. As a result, the other push plate moves away from the other stopper, and the movement of the end cylinder relative to the exterior cylinder is transmitted to the screw shaft via the other push plate, the disc spring unit, one push plate, and one stopper. Is done. Thereby, a nut and a rotation mass rotate in one as a screw axis moves to the opposite side to a nut. As described above, in the conventional mass damper, the relative displacement between the first and second portions is applied to the rotating mass via the disc spring unit in both cases where the compressive force acts and the tensile force acts. An additional vibration system composed of a disc spring unit and a rotating mass is configured. This is to make it possible to connect the mass damper to the first and second portions without using an attachment member having a spring function such as a steel material generally used to configure the additional vibration system together with the rotating mass.

JP 2012-189104 A

  As described above, in the conventional mass damper, in order to transmit the relative displacement between the first and second parts due to the vibration of the structure to the rotating mass through the disc spring unit, the end cylinder, the lid, A complicated configuration such as a plurality of keys is employed. Further, not only the screw shaft and nut but also the rotating mass is accommodated in the exterior cylinder. As a result, the configuration of the entire mass damper becomes very complicated.

  The present invention has been made in order to solve the above-described problems, and a rotating mass and an elastic body for forming an additional vibration system can be connected in series with each other and can be configured relatively easily. The purpose is to provide a mass damper.

  In order to achieve the above object, an invention according to claim 1 is a mass damper provided between a first part and a second part in a system including a structure for suppressing vibration of the structure. A cylindrical main body, a rotary mass provided integrally with the main body, and a first portion connected to the main body and extending in the axial direction of the main body; A screw shaft that is movably partly and coaxially accommodated, is screwed to the screw shaft via a ball, and is connected to a nut attached to one part of the main body and a second part. A rod that extends in the direction and is accommodated partially and coaxially so as to be movable in the axial direction at the other portion in the axial direction of the main body, and is provided integrally with the rod and rotatably supports the main body, Housed in the other part of the main body so as to be movable in the axial direction And a pair of thrust bearings that are accommodated in the other part of the main body part, are coaxially provided in the main body part, and are respectively disposed on both sides in the axial direction of the flange, and a plurality of laminated axially Consists of a disc spring, accommodated in the other part of the main body, the rod is inserted, and is arranged between the flange and one of the pair of thrust bearings and between the flange and the other of the pair of thrust bearings, respectively A pair of disc spring units, and the relative displacement between the first part and the second part generated by the vibration of the structure is a screw shaft, nut, rod, flange, disc spring unit, and thrust bearing. Is transmitted to the main body part in a state converted into a rotational motion, whereby the main body part and the rotary mass rotate with respect to the rod, and the disc spring unit is flanged. Characterized in that it is pressed in the axial direction in the fine body portion.

  According to this configuration, the rotating mass is integrally provided on the cylindrical main body, and the screw shaft is partially and coaxially movable at one site in the axial direction of the main body so as to be movable in the axial direction. It is housed in a shape. The screw shaft is connected to the first portion and extends in the axial direction. A nut attached to one part of the main body is screwed onto the screw shaft via a ball. The rod is housed partially and coaxially in the other axial portion of the main body so as to be movable in the axial direction. The rod is connected to the second portion, extends in the axial direction, and supports the main body portion rotatably. Moreover, the rod is integrally provided with a flange, and this flange is accommodated in the other part of the main body so as to be movable in the axial direction. A pair of thrust bearings and a pair of disc spring units are housed in the other part of the main body. The pair of thrust bearings are coaxially provided on the main body and are respectively disposed on both sides of the flange in the axial direction. Each of the pair of disc spring units is composed of a plurality of disc springs stacked in the axial direction, and is between the flange and one of the pair of thrust bearings and between the flange and the other of the pair of thrust bearings. And a rod is inserted.

  Relative displacement between the first part and the second part generated by the vibration of the structure is transmitted to the screw shaft and the rod, and is further subjected to rotational movement via the nut, flange, disc spring unit and thrust bearing. The converted data is transmitted to the main body. Thereby, since a main-body part and a rotation mass rotate together with respect to a rod and the rotation inertial mass effect by a rotation mass is acquired, the vibration of a structure can be suppressed appropriately. At that time, since the disc spring unit is pressed by the flange and the main body and exhibits its rigidity, an additional vibration system can be configured by the rotating mass and the disc spring unit.

  Accordingly, it is possible to connect the mass damper to the first and second portions without using an attachment member having a spring function such as a steel material generally used to configure the additional vibration system together with the rotating mass. In this case, along with transmission of the relative displacement between the first part and the second part to the rotating mass, an axial pressing force (axial load) acts between the disc spring unit and the main body part. Since the thrust bearing is provided on the main body, the main body and the rotary mass can be appropriately rotated with respect to the rod.

  Further, as is clear from the above description, the mass damper according to the present invention has the same function as the conventional mass damper described above, and includes a disc spring unit and a rotating mass as an elastic body for constituting the additional vibration system. They can be connected to each other in series. On the other hand, unlike conventional mass dampers, it does not require complicated structures such as end cylinders, lids, and multiple keys, and the rotating mass is provided integrally with the main body, not separately. It can be configured relatively easily.

  In addition, unlike a conventional mass damper, for example, when the rotating mass is provided integrally without being housed in the main body portion, when adjusting the rotational inertial mass of the rotating mass, without removing the rotating mass from the main body portion, The adjustment can be easily performed. Further, in this case, for the same reason, in order to obtain a large rotating inertial mass effect of the rotating mass, even if the area of the surface orthogonal to the axial direction is increased, unlike the conventional mass damper, the axial direction of the main body portion Since the area of the plane orthogonal to does not have to be larger than that of the rotating mass, the entire mass damper can be reduced in size.

  According to a second aspect of the present invention, in the mass damper according to the first aspect, the main body portion is disposed on the cylindrical peripheral wall extending in the axial direction and the other portion of the main body portion in a state of being spaced apart from each other in the axial direction. The fluid chamber is defined by the pair of wall portions and the peripheral wall in the other part of the main body portion, and each of the pair of wall portions has an axial direction. The rod is inserted into the insertion hole, so that the main body is rotatably supported, and the flange is slidable and slidable in the axial direction in the fluid chamber. The fluid chamber is divided into a first fluid chamber and a second fluid chamber, and the pair of thrust bearings are respectively provided on the pair of wall portions and are respectively accommodated in the first and second fluid chambers, A pair of disc spring units are provided in the first and second fluid chambers. In order to adjust the pressure of the viscous fluid contained in the first and second fluid chambers and the flanges provided in the first and second fluid chambers, respectively. And a pressure regulating valve for communicating the two fluid chambers with each other.

  According to this configuration, the main body unit integrally includes a cylindrical peripheral wall extending in the axial direction and a pair of wall units disposed on the other part of the main body unit in a state of being spaced apart from each other in the axial direction. Have. A fluid chamber is defined in the other part of the main body by a peripheral wall and a pair of walls, and an insertion hole penetrating in the axial direction is formed in each of the pair of walls. The rod is inserted into the insertion hole, thereby supporting the main body portion rotatably.

  The flange integral with the rod is provided in the fluid chamber so as to be rotatable and slidable in the axial direction, and partitions the fluid chamber into a first fluid chamber and a second fluid chamber. The pair of thrust bearings are provided on the pair of wall portions, respectively, and are accommodated in the first and second fluid chambers, respectively, and the pair of disc spring units are accommodated in the first and second fluid chambers, respectively. ing. The first and second fluid chambers are filled with a viscous fluid, and the flange is adjusted so that the fluid chambers communicate with each other in order to adjust the pressure of the viscous fluid in the first and second fluid chambers. A pressure valve is provided.

  As described above, the fluid chamber defined in the other part of the main body is filled with the viscous fluid, and the flange integral with the rod is provided so as to be slidable in the axial direction. The pressure of the viscous fluid in the partitioned first and second fluid chambers is adjusted by a pressure regulating valve. For this reason, when the flange slides in the fluid chamber as the relative displacement between the first portion and the second portion is transmitted to the rod and the screw shaft, the viscosity inside one of the first and second fluid chambers. Since the fluid is pressed by the flange and the pressure is adjusted by the pressure regulating valve, it is possible to further obtain a viscous damping effect by the viscous fluid, and more appropriately suppress the vibration of the structure.

  In order to achieve the above object, an invention according to claim 3 is a mass damper provided between a first part and a second part in a system including a structure for suppressing vibration of the structure, It is connected to the cylindrical main body, the rotary mass provided integrally with the main body, and the first portion, extends in the axial direction of the main body, and moves to one axial portion of the main body in the axial direction. A screw shaft that is partly and coaxially accommodated as possible, a nut that is screwed onto the screw shaft via a ball, and that is connected to one part of the main body and a second part, and is axially connected A rod that is partially and coaxially accommodated so as to be movable in the axial direction at the other portion in the axial direction of the main body, and a rod that rotatably supports the main body, and is provided integrally with the rod. To the other part of the A rod piston accommodated in a possible manner and a pair of elastic bodies respectively disposed on both sides of the rod piston in the axial direction and accommodated in the other portion of the main body, and the other portion of the main body in the axial direction It is slidably accommodated, and is disposed between the rod piston and one of the pair of elastic bodies, and between the rod piston and the other of the pair of elastic bodies, and inside the other part of the main body. A pair of pistons that define a first fluid chamber and a second fluid chamber, respectively, between the rod piston, move in the axial direction with respect to the rod, and rotate with respect to at least one of the main body and the rod And a fluid filled in the first and second fluid chambers, and the relative displacement between the first part and the second part generated by the vibration of the structure is a screw shaft, nut, rod, rod piston It is transmitted to the main body through a fluid, a piston, and an elastic body in a state of being converted into rotational motion, whereby the main body and the rotating mass rotate, and the elastic body is pressed in the axial direction by the piston and the main body. It is characterized by that.

  According to this configuration, the rotating mass is integrally provided on the cylindrical main body, and the screw shaft is partially and coaxially movable at one site in the axial direction of the main body so as to be movable in the axial direction. It is housed in a shape. The screw shaft is connected to the first portion and extends in the axial direction. A nut attached to one part of the main body is screwed onto the screw shaft via a ball. The rod is housed partially and coaxially in the other axial portion of the main body so as to be movable in the axial direction. The rod is connected to the second portion, extends in the axial direction, and supports the main body portion rotatably. Moreover, the rod piston is integrally provided in the rod, and this rod piston is accommodated in the other part of the main body so as to be rotatable and slidable in the axial direction.

  A pair of elastic bodies and a pair of pistons are accommodated in the other part of the main body, and these pair of elastic bodies are respectively disposed on both sides in the axial direction of the rod piston. The pair of pistons are disposed between the rod piston and one of the pair of elastic bodies and between the rod piston and the other of the pair of elastic bodies, respectively, and the axis of the other part of the main body portion Slidable in the direction, movable in the axial direction relative to the rod, and rotatable relative to at least one of the main body and the rod. A first fluid chamber and a second fluid chamber are defined in the other part of the main body between the rod piston and one of the pair of pistons and between the other of the pair of pistons. These first and second fluid chambers are filled with fluid.

  The relative displacement between the first part and the second part generated by the vibration of the structure is transmitted to the screw shaft and the rod, and further rotated through the nut, the rod piston, the fluid, the piston, and the elastic body. It is transmitted to the main body in a state converted into motion. Thereby, a main-body part and a rotation mass rotate together, and the vibration of a structure can be suppressed appropriately by the rotation inertial mass effect by a rotation mass being acquired. At that time, the elastic body is pressed by the fluid, the piston, and the main body, and exhibits its rigidity. Therefore, the additional vibration system can be configured by the rotating mass and the elastic body.

  Accordingly, it is possible to connect the mass damper to the first and second portions without using an attachment member having a spring function such as a steel material generally used to configure the additional vibration system together with the rotating mass. In this case, the movement of the rod and the rod piston relative to the screw shaft is transmitted to the main body via a fluid that can be sheared in the circumferential direction, and the piston that is pressed via the fluid as the rod piston moves is the main body. Since it can rotate with respect to a part and / or a rod, a main-body part and a rotation mass can be appropriately rotated with respect to a rod.

  Further, as is apparent from the above description, the mass damper according to the present invention has the same function as the conventional mass damper described above, similarly to the mass damper according to the first aspect of the present invention, and constitutes an additional vibration system. The rotating mass and the elastic body can be connected to each other in series. On the other hand, unlike conventional mass dampers, it does not require complicated structures such as end cylinders, lids, and multiple keys, and the rotating mass is provided integrally with the main body, not separately. It can be configured relatively easily.

  Further, like the mass damper of the invention according to claim 1, unlike the conventional mass damper, for example, when the rotating mass is provided integrally without being housed in the main body, the rotational inertia mass of the rotating mass is adjusted. The adjustment can be easily performed without taking out the rotating mass from the main body. Further, in this case, for the same reason, in order to obtain a large rotating inertial mass effect of the rotating mass, even if the area of the surface orthogonal to the axial direction is increased, unlike the conventional mass damper, the axial direction of the main body portion Since the area of the plane orthogonal to does not have to be larger than that of the rotating mass, the entire mass damper can be reduced in size.

  According to a fourth aspect of the present invention, there is provided the mass damper according to the third aspect, wherein the first and second fluid chambers are provided on the rod piston to prevent the fluid pressure in the first and second fluid chambers from becoming excessive. It further has a relief valve for communicating with each other.

  As described above, in the mass damper, as the relative displacement between the first part and the second part is transmitted to the screw shaft and the rod, the fluid in the first and second fluid chambers is pressed by the rod piston and the piston. Is done. For this reason, since the pressure of the fluid becomes a load and acts on the rod and the screw shaft in the axial direction, the load (hereinafter referred to as “axial load”) increases as the pressure of the fluid increases. According to the above-described configuration, the relief valve for preventing the pressure of the fluid in the first and second fluid chambers from being increased is provided in the rod piston, so that the shaft load can be prevented from being increased excessively. . Further, the first and second fluid chambers are communicated with each other by the relief valve, so that a viscous damping effect by the fluid can be further obtained.

  In order to achieve the above object, an invention according to claim 5 is a mass damper provided between a first part and a second part in a system including a structure for suppressing vibration of the structure, It is connected to the cylindrical main body, the rotary mass provided integrally with the main body, and the first portion, extends in the axial direction of the main body, and moves to one axial portion of the main body in the axial direction. A screw shaft that is partly and coaxially accommodated as possible, a nut that is screwed onto the screw shaft via a ball, and that is connected to one part of the main body and a second part, and is axially connected A support portion that is partially and coaxially accommodated in the other axially movable portion of the main body portion so as to be movable in the axial direction and rotatably supports the main body portion, and one of the main body portion and the support portion. And are spaced apart from each other in the axial direction. A pair of first engaging portions disposed in a state where the second engaging portion is provided, and a second engaging portion disposed between the pair of first engaging portions, A pair of elastic bodies respectively disposed between one of the first engaging portions and the second engaging portion and between the other of the pair of first engaging portions and the second engaging portion. Provided, and relative displacement between the first part and the second part generated by the vibration of the structure is caused via the screw shaft, the nut, the support part, the first engagement part, the elastic body, and the second engagement part. Then, it is transmitted to the main body part in a state converted into a rotational motion, whereby the main body part and the rotating mass rotate with respect to the support part, and the elastic body is pressed in the axial direction by the first and second engaging parts. Further, a thrust bearing provided coaxially with the main body on the relative displacement transmission path composed of the first engagement portion, the elastic body and the second engagement portion is further exposed. Characterized in that it comprises.

  According to this configuration, the rotating mass is integrally provided on the cylindrical main body, and the screw shaft is partially and coaxially movable at one site in the axial direction of the main body so as to be movable in the axial direction. It is housed in a shape. The screw shaft is connected to the first portion and extends in the axial direction. A nut attached to one part of the main body is screwed onto the screw shaft via a ball. In the other part of the main body in the axial direction, a support part is accommodated partially and coaxially so as to be movable in the axial direction. The support portion is connected to the second portion, extends in the axial direction, and rotatably supports the main body portion. One of the main body part and the support part is integrally provided with a pair of first engaging parts arranged in a state of being spaced apart from each other in the axial direction, and the other of the main body part and the support part is provided with a pair of first engagement parts. The 2nd engaging part arrange | positioned between the 1st engaging parts is provided integrally. In addition, a pair of elastic bodies are provided between one of the pair of first engaging portions and the second engaging portion, and between the other of the pair of first engaging portions and the second engaging portion, respectively. Has been placed.

  Relative displacement between the first part and the second part generated by the vibration of the structure is transmitted to the screw shaft and the support part, and further, the nut, the first engagement part, the elastic body, and the second engagement. Via the part, it is transmitted to the main part in a state converted into a rotational motion. Thereby, since a main-body part and a rotation mass rotate together with respect to a support part and the rotation inertial mass effect by a rotation mass is acquired, the vibration of a structure can be suppressed appropriately. At this time, since the elastic body is pressed by the first and second engaging portions and exhibits its rigidity, the additional vibration system can be configured by the rotating mass and the elastic body.

  Accordingly, it is possible to connect the mass damper to the first and second portions without using an attachment member having a spring function such as a steel material generally used to configure the additional vibration system together with the rotating mass. In this case, along with the transmission of the relative displacement between the first part and the second part to the rotating mass, on the above-described relative displacement transmission path composed of the elastic body and the first and second engaging portions, A pressing force (axial load) is generated. According to the configuration described above, since the thrust bearing is provided on the transmission path, the main body portion and the rotation mass can be appropriately rotated with respect to the support portion.

  Further, as is apparent from the above description, the mass damper according to the present invention has the same function as the conventional mass damper described above, similarly to the mass damper according to the first aspect of the present invention, and constitutes an additional vibration system. The rotating mass and the elastic body can be connected to each other in series. On the other hand, unlike conventional mass dampers, it does not require complicated structures such as end cylinders, lids, and multiple keys, and the rotating mass is provided integrally with the main body, not separately. It can be configured relatively easily.

  In addition, unlike a conventional mass damper, for example, when the rotating mass is provided integrally without being housed in the main body portion, when adjusting the rotational inertial mass of the rotating mass, without removing the rotating mass from the main body portion, The adjustment can be easily performed. Further, in this case, for the same reason, in order to obtain a large rotating inertial mass effect of the rotating mass, even if the area of the surface orthogonal to the axial direction is increased, unlike the conventional mass damper, the axial direction of the main body portion Since the area of the plane orthogonal to does not have to be larger than that of the rotating mass, the entire mass damper can be reduced in size.

  In order to achieve the object, an invention according to claim 6 is a mass damper provided between a first part and a second part in a system including a structure for suppressing vibration of the structure, A main body part integrally formed with a cylindrical connecting part extending in the direction, and a pair of wall parts disposed at one part in the axial direction so as to be spaced apart from each other in the axial direction, and integrally with the main body part A rotating mass provided; and a screw shaft that is connected to the first portion and extends in the axial direction, and is partially and coaxially accommodated in the other axial portion of the main body so as to be movable in the axial direction. , Screwed to the screw shaft via a ball, coupled to a nut attached to the other part of the main body part, and the second part, extending in the axial direction, and extending to one part of the main body part in the axial direction The body part is movably partly and coaxially accommodated. A pair of support portions that are rotatably supported, a pair of pressing portions that are provided integrally with the support portion and are spaced apart from each other in the axial direction, and that are movable in the axial direction with respect to the main body portion; The elastic body disposed between the pressing portions, between one of the pair of pressing portions and the elastic body, and between the other of the pair of pressing portions and the elastic body, respectively, with respect to the main body portion and the support portion It is configured to be movable in the axial direction, and as the support portion moves in the axial direction with respect to the main body portion, the pressing portion is pressed in the axial direction, and the pressing force of the pressing portion is reduced by the elastic body. A pair of transmitting portions that transmit to the wall portion, and the relative displacement between the first portion and the second portion that is generated along with the vibration of the structure is a screw shaft, a nut, a support portion, a pressing portion, Via the elastic body, the transmission part, and the wall part, the main body part is converted into a rotational motion. Thus, the main body and the rotating mass rotate with respect to the support, and the thrust provided coaxially with the main body on the relative displacement transmission path composed of the pressing part, the elastic body, the transmission part and the wall part. Further comprising a bearing.

  According to this configuration, the main body portion includes a cylindrical connecting portion extending in the axial direction, and a pair of wall portions disposed at one portion in the axial direction so as to be spaced apart from each other in the axial direction. The main body is integrally provided with a rotating mass. In addition, a screw shaft is accommodated in the other portion in the axial direction of the main body portion so as to be movable in the axial direction and is coaxially connected. The screw shaft is connected to the first portion, It extends in the axial direction. A nut attached to the other part of the main body is screwed onto the screw shaft via a ball. In one part of the main body in the axial direction, a support part is accommodated partially and coaxially so as to be movable in the axial direction. The support portion is connected to the second portion, extends in the axial direction, and rotatably supports the main body portion.

  In addition, the support portion is integrally provided with a pair of pressing portions, and the pair of pressing portions are movable in the axial direction with respect to the main body portion, and are spaced apart from each other in the axial direction. Has been placed. An elastic body is disposed between the pair of pressing portions, and a pair of transmission portions is provided between one of the pair of pressing portions and the elastic body, and between the other of the pair of pressing portions and the elastic body. Each is arranged. The pair of transmission parts are configured to be movable in the axial direction with respect to the main body part and the support part, and as the support part moves in the axial direction with respect to the main body part, the integral pressing with the support part is performed. The pressing portion is pressed in the axial direction, and the pressing force of the pressing portion is transmitted to the wall portion through the elastic body.

  Relative displacement between the first part and the second part generated by the vibration of the structure is caused by rotational movement via the screw shaft, nut, support part, pressing part, elastic body, transmission part, and wall part. The converted data is transmitted to the main body. Thereby, since a main-body part and a rotation mass rotate together with respect to a support part and the rotation inertial mass effect by a rotation mass is acquired, the vibration of a structure can be suppressed appropriately. At that time, as is apparent from the operation of the pressing portion, the elastic body and the transmission portion accompanying the movement of the support portion described above, the elastic body is pressed by the pressing portion, the transmission portion and the wall portion, and exhibits its rigidity. An additional vibration system can be constituted by the rotating mass and the elastic body.

  Accordingly, it is possible to connect the mass damper to the first and second portions without using an attachment member having a spring function such as a steel material generally used to configure the additional vibration system together with the rotating mass. In this case, along with the transmission of the relative displacement between the first part and the second part to the rotating mass, the axial pressing force on the relative displacement transmission path composed of the pressing part, the elastic body, the transmission part and the wall part. (Axial load) occurs. According to the configuration described above, since the thrust bearing is provided on the transmission path, the main body portion and the rotation mass can be appropriately rotated with respect to the support portion.

  Further, as is apparent from the above description, the mass damper according to the present invention has the same function as the conventional mass damper described above, similarly to the mass damper according to the first aspect of the present invention, and constitutes an additional vibration system. The rotating mass and the elastic body can be connected to each other in series. On the other hand, unlike conventional mass dampers, it does not require complicated structures such as end cylinders, lids, and multiple keys, and the rotating mass is provided integrally with the main body, not separately. It can be configured relatively easily.

  In addition, unlike a conventional mass damper, for example, when the rotating mass is provided integrally without being housed in the main body portion, when adjusting the rotational inertial mass of the rotating mass, without removing the rotating mass from the main body portion, The adjustment can be easily performed. Further, in this case, for the same reason, in order to obtain a large rotating inertial mass effect of the rotating mass, even if the area of the surface orthogonal to the axial direction is increased, unlike the conventional mass damper, the axial direction of the main body portion Since the area of the plane orthogonal to does not have to be larger than that of the rotating mass, the entire mass damper can be reduced in size.

  The invention according to claim 7 is the mass damper according to any one of claims 3 to 6, wherein the elastic body is a disc spring unit including a plurality of disc springs stacked in the axial direction.

  According to this structure, it is a disc spring unit comprising a plurality of disc springs in which the elastic body is laminated in the axial direction. Therefore, when setting the rigidity of the elastic body in order to adjust the natural frequency of the additional vibration system described in the inventions according to claims 3, 5 and 6, the setting is made based on the number of the disc springs and the way of lamination. It can be done easily just by changing.

  The invention according to claim 8 is the mass damper according to any one of claims 1 to 7, further comprising an adjustment mass that is attached to at least one of the main body and the rotation mass and adjusts the rotation inertia mass of the rotation mass. It is characterized by providing.

  According to this configuration, since the adjustment mass for adjusting the rotational inertia mass of the rotary mass is attached to at least one of the main body and the rotary mass, the rotary inertia mass of the rotary mass can be adjusted more easily. Can do.

  The invention according to claim 9 is the mass damper according to any one of claims 1 to 8, characterized in that the main body portion and the rotating mass are formed of members common to each other.

  According to this configuration, since the main body portion and the rotating mass are configured by members that are common to each other, the number of parts can be reduced accordingly, and thus the manufacturing cost can be reduced, and the mass damper can be further simplified. Can be configured.

It is sectional drawing which shows the mass damper by 1st Embodiment of this invention. It is a figure which shows roughly the mass damper of FIG. 1 with a part of building which applied this. It is a model figure which shows the mass damper of FIG. (A)-(i) It is a figure which shows an example of the variation of the number of the disc springs of a test apparatus, and the method of lamination | stacking. It is a figure which shows the relationship between the deflection of a disc spring, and a load in each of the variation shown to Fig.4 (a)-(i). It is sectional drawing which shows the mass damper by 2nd Embodiment of this invention. It is sectional drawing which expands and shows the 1st pressure regulation valve, the 2nd pressure regulation valve, etc. of the mass damper of FIG. It is a model figure of the mass damper of FIG. It is sectional drawing which shows the modification of the mass damper of FIG. It is sectional drawing which shows the mass damper by 3rd Embodiment of this invention. It is sectional drawing which expands and shows the 1st relief valve, 2nd relief valve, etc. of the mass damper of FIG. FIG. 11 is a model diagram of the mass damper of FIG. 10 when (a) the first and second relief valves are not opened, and (b) the first or second relief valve is opened. It is a figure which shows the modification of the mass damper of FIG. It is sectional drawing which shows the mass damper by 4th Embodiment of this invention. (A) It is sectional drawing which shows the modification of the mass damper of FIG. 1 different from FIG. 9, (b) It is sectional drawing which shows the modification of the mass damper of FIG. It is sectional drawing which shows the mass damper by 5th Embodiment of this invention. It is sectional drawing which shows the mass damper by 6th Embodiment of this invention. It is sectional drawing which shows the mass damper of FIG. 17 in case a compressive force acts.

  Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the drawings. FIG. 1 shows a mass damper 1 according to a first embodiment of the present invention. Hereinafter, for convenience, the left side and the right side in FIG. 1 will be described as “left” and “right”, respectively. As shown in FIG. 1, the mass damper 1 is provided on a cylindrical main body 2, a rotary mass provided integrally with the main body 2, and a left portion of the main body 2, and rotatably supports the main body 2. And a ball screw 4 provided on the right side of the main body 2.

  The main body 2 is made of a material having a relatively large specific gravity, for example, iron, and is provided between the left and right side walls 2a and 2b and both side walls 2a and 2b, and extends in the left and right direction (axial direction). The main body 2 and the rotating mass are formed of members that are common to each other. That is, the main body 2 is also used as a rotating mass. A donut plate-shaped accommodation wall 2d is integrally provided on the left side of the peripheral wall 2c. The left and right side walls 2a, 2b and the housing wall 2d are formed with insertion holes 2e, 2f, 2g penetrating in the left-right direction, respectively, and these insertion holes 2e-2g are arranged coaxially with the peripheral wall 2c. Yes.

  The rod 3 is inserted into the insertion holes 2e and 2g of the main body 2 via the sliding members 5 and 5 and extends in the left-right direction, and supports the main body 2 rotatably. Further, the rod 3 is accommodated in the left part of the main body part 2 so as to be movable in the left-right direction and partially coaxially, and protrudes leftward from the main body part 2. The sliding members 5 and 5 are made of a highly slippery material such as a fluororesin. In addition, a disc-shaped flange 6 is integrally and coaxially provided at the center of the rod 3, and the flange 6 is provided in a storage chamber 2h defined by the left side wall 2a, the peripheral wall 2c, and the storage wall 2d. The rod 3 is accommodated so as to be movable in the left-right direction.

  The ball screw 4 has a screw shaft 4a and a nut 4c that is screwed onto the screw shaft 4a via a large number of balls 4b. The screw shaft 4a is inserted into the insertion hole 2f of the right side wall 2b via the sliding material 5 and extends in the left-right direction. Further, the screw shaft 4a is accommodated in the right part of the main body part 2 so as to be movable in the left-right direction and partially coaxially, and protrudes rightward from the main body part 2. The nut 4c is coaxially attached to the right surface of the right side wall 2b, and a screw hole at the center thereof communicates with the insertion hole 2f.

  The mass damper 1 is further accommodated in the accommodation chamber 2h, and left and right thrust bearings 7L and 7R provided coaxially on the left side wall 2a and the accommodation wall 2d, and left and right disc spring units accommodated in the accommodation chamber 2h. 8L and 8R are provided. Each disc spring unit 8L (8R) is composed of a plurality of disc springs 8a stacked in the left-right direction, and the rod 3 is inserted into the center hole thereof. The left disc spring unit 8L is disposed between the flange 6 and the left thrust bearing 7L, and the right disc spring unit 8R is disposed between the flange 6 and the right thrust bearing 7R. The rigidity of each of the left and right disc spring units 8L and 8R is determined by the number of disc springs 8a and the manner of lamination. FIG. 1 shows an example in which eight disc springs 8a are laminated in series. The setting of the number of disc springs 8a and the way of stacking will be described later.

  A first attachment FL1 and a second attachment FL2 are attached to the left end of the rod 3 and the right end of the screw shaft 4a via universal joints, respectively. These universal joints generate a frictional force so that the rod 3 and the screw shaft 4a do not rotate with respect to the first and second fixtures FL1 and FL2 due to the torque generated by the reaction force of the rotating main body 2 as will be described later. Have.

  As shown in FIG. 2, the mass damper 1 having the above configuration is connected to the upper beam BU and the lower beam BD of the building B in a brace shape, for example. In this case, the first fixture FL1 is attached to the first connecting member EN1 fixed to the joint between the upper beam BU and the left column PL, and the second fixture FL2 is attached to the lower beam BD and the right column PR. Are attached to the second connecting member EN2 fixed to the joint.

  When the building B vibrates, a relative displacement occurs between the upper and lower beams BU and BD. When a tensile force acts on the mass damper 1, the rod 3 and the screw shaft 4a are moved to the left with respect to the main body 2. And move to the right respectively. Accordingly, the left disc spring unit 8L is pressed by the flange 6 integral with the rod 3 and the left thrust bearing 7L attached to the left side wall 2a of the main body 2, and the nut 4c screwed into the screw shaft 4a. Rotates together with the main body 2 with respect to the rod 3 and the screw shaft 4a. Thus, when a tensile force acts on the mass damper 1 in accordance with the vibration of the building B, the relative displacement between the upper and lower beams BU, BD is as follows: rod 3, flange 6, left disc spring unit 8L, left thrust. It is transmitted to the main body 2 through the bearing 7L, the screw shaft 4a, and the nut 4c in a state of being converted into a rotational motion, whereby the main body 2 that is also used as a rotating mass rotates.

  On the other hand, when a compressive force is applied to the mass damper 1, the rod 3 and the screw shaft 4 a move to the right and left with respect to the main body 2, respectively. Accordingly, the right disc spring unit 8R is pressed by the flange 6 and the right thrust bearing 7R attached to the housing wall 2d of the main body 2, and the nut 4c is moved together with the main body 2 and the rod 3 and It rotates with respect to the screw shaft 4a. Thus, when a compressive force acts on the mass damper 1 with the vibration of the building B, the relative displacement between the upper and lower beams BU, BD is as follows: rod 3, flange 6, right disc spring unit 8R, right thrust. It is transmitted to the main body 2 through the bearing 7R, the screw shaft 4a and the nut 4c in a state of being converted into rotational motion, whereby the main body 2 rotates.

  As is clear from the operation of the mass damper 1 described above, in the mass damper 1, the main body 2 that is also used as a rotating mass and the left disc spring unit 8L (right disc spring unit 8R) are connected in series with each other. . For this reason, the model diagram of the mass damper 1 is expressed as shown in FIG. 3, for example.

  In this manner, in the mass damper 1, an additional vibration system can be configured by the main body 2 and the left disk spring unit 8L (right disk spring unit 8R). The natural frequency of this additional vibration system is based on a fixed point theory. The frequency is set so as to tune (resonate) with the natural frequency (for example, the primary natural frequency) of the structure. The natural frequency f of the additional vibration system is f = sqrt {K / M} / (2π) using the rotational inertia mass M of the main body 2 and the rigidity K of the left disc spring unit 8L (right disc spring unit 8R). The natural frequency f of the additional vibration system is set by adjusting the rotational inertia mass M of the main body 2 and the rigidity K of the left disc spring unit 8L (right disc spring unit 8R).

  In this case, the rotation inertia mass M of the main body 2 is adjusted by adjusting at least one of the left and right side walls 2a, 2b, the peripheral wall 2c and the housing wall 2d, and the pitch of the ball screws 4 of the main body 2. This is done by setting. Further, the adjustment of the rigidity K of the left disc spring unit 8L (right disc spring unit 8R) is performed by setting the number of disc springs 8a and the way of stacking.

  4A to 4I show an example of variations of the number of disc springs 8a and the way of stacking (series / parallel). FIG. 5 shows the deflection (mm) of the disc springs 8a in each variation. A load (kN) relationship (hereinafter referred to as “deflection-load relationship”) is shown. In FIGS. 4B to 4I, only one disc spring 8a is attached for convenience. Further, in FIG. 5, Ra represents the deflection-load relationship when there is one disc spring 8a (FIG. 4A), and Rb is when two disc springs 8a are stacked in series (FIG. 4). (B)) represents the deflection-load relationship, and Rc represents the deflection-load relationship when the three disc springs 8a are stacked in series (FIG. 4C).

  Further, in FIG. 5, Rd represents a deflection-load relationship when two disc springs 8a are laminated in parallel (FIG. 4D), and Re is a pair of two disc springs 8a laminated in parallel. Represents the deflection-load relationship when two pairs are stacked in series (FIG. 4E), and Rf is when three sets are stacked in series with two disk springs 8a stacked in parallel as one set (FIG. 4 (f)) represents a deflection-load relationship. In FIG. 5, Rg represents a deflection-load relationship when three disc springs 8a are stacked in parallel (FIG. 4G), and Rh is a set of three disc springs 8a stacked in parallel. Represents the deflection-load relationship when two pairs are stacked in series as shown in FIG. 4 (h), and Ri is when three sets are stacked in series with three disc springs 8a stacked in parallel as one set. The deflection-load relationship of (FIG. 4 (i)) is represented.

  If the rigidity of the disc spring 8a is ks, when n disc springs 8a are stacked in parallel, the stiffness K of the left disc spring unit 8L (right disc spring unit 8R) is n · ks. When n disc springs 8a are stacked in series, the rigidity K of the left disc spring unit 8L (right disc spring unit 8R) is ks / (n + 1). By setting the number of disc springs 8a and the way of stacking (series / parallel) using various variations as shown in FIG. 4 as appropriate, the natural frequency f of the additional vibration system is set to the natural frequency of the structure. The rigidity K of the left disc spring unit 8L (right disc spring unit 8R) is adjusted so as to synchronize with.

  As described above, according to the first embodiment, the cylindrical main body 2 is also used as a rotating mass, and the screw shaft 4a is a part of the right portion of the main body 2 that is movable in the axial direction. And coaxially. The screw shaft 4a is connected to the lower beam BD and extends in the axial direction. Moreover, the nut 4c attached to the right side wall 2b of the main-body part 2 is screwingly engaged with the screw shaft 4a via the ball 4b. The rod 3 is accommodated in the left part of the main body 2 partially and coaxially so as to be movable in the axial direction. The rod 3 is connected to the upper beam BU, extends in the axial direction, and rotatably supports the main body 2.

  The rod 3 is integrally provided with a flange 6. The flange 6 is accommodated in the left part of the main body 2 so as to be movable in the axial direction. The left and right thrust bearings 7L and 7R and the left and right disc spring units 8L and 8R are accommodated in the left part of the main body 2. These left and right thrust bearings 7 </ b> L and 7 </ b> R are coaxially provided on the main body 2 and are disposed on both sides of the flange 6 in the axial direction. The left and right disc spring units 8L and 8R are each composed of a plurality of disc springs 8a stacked in the axial direction, between the flange 6 and the left thrust bearing 7L, and between the flange 6 and the right thrust bearing 7R. And the rod 3 is inserted.

  The relative displacement between the upper and lower beams BU and BD generated by the vibration of the building B is transmitted to the screw shaft 4a and the rod 3, and further, the nut 4c, the flange 6, the disc spring unit 8L (8R) and the thrust bearing. It is transmitted to the main body 2 through 7L (7R) in a state converted into rotational motion. Thereby, since the main-body part 2 used also as a rotation mass rotates with respect to the rod 3, the rotation inertial mass effect by the main-body part 2 is acquired, Therefore The vibration of the building B can be suppressed appropriately. At that time, the disc spring unit 8L (8R) is pressed by the flange 6 and the main body 2 and exhibits its rigidity, so that the additional vibration system can be constituted by the main body 2 and the disc spring unit 8L (8R). . Thereby, it becomes possible to connect the mass damper 1 to the upper and lower beams BU and BD without using an attachment member having a spring function such as a steel material generally used for constituting the additional vibration system together with the rotating mass. . In this case, an axial pressing force (axial load) acts between the disc spring unit 8L (8R) and the main body 2 with transmission of relative displacement between the upper and lower beams BU and BD to the main body 2. However, since the thrust bearing 7L (7R) is provided between the two 8L (8R) and 2, the main body 2 can be appropriately rotated with respect to the rod 3.

  Further, as is apparent from the above description, the mass damper 1 has the same function as the conventional mass damper described above, and the main body 2 (rotary mass) and the disc spring unit 8L ( 8R) can be connected in series with each other. On the other hand, unlike the conventional mass damper, a complicated configuration such as an end cylinder, a lid, and a plurality of keys is not required, so that the mass damper 1 can be configured relatively easily. In this case, since the main body 2 and the rotating mass are configured by members that are common to each other, the number of parts can be reduced accordingly, and thus the manufacturing cost can be reduced, and the mass damper 1 can be configured more simply. can do.

  In addition, unlike the conventional mass damper, the main body 2 and the rotary mass are made of a common member, and the rotary mass is not accommodated in the main body 2. Therefore, the rotary inertia mass of the rotary mass can be easily adjusted. Can do. For the same reason, in order to obtain a large rotational inertial mass effect of the rotating mass, even if the area of the surface orthogonal to the axial direction is increased, the area of the surface orthogonal to the axial direction of the main body 2 differs from the conventional mass damper. Can be made smaller than the rotating mass, so that the entire mass damper 1 can be downsized.

  Furthermore, since the left and right disc spring units 8L and 8R composed of a plurality of disc springs 8a stacked in the axial direction are used as the elastic body in the present invention, the left and right disc frequency units f of the additional vibration system are adjusted in order to adjust the natural frequency f. In setting the rigidity K of the disc spring units 8L and 8R, the setting can be easily performed only by changing the number of the disc springs 8a and the way of lamination.

  Next, the mass damper 11 according to the second embodiment of the present invention will be described with reference to FIGS. Compared with the first embodiment, the mass damper 11 includes a rod 12 integrally provided with a piston 12 instead of the flange 6, and the piston 12 allows the left side wall 2 a, the peripheral wall 2 c, and the housing wall to be integrated. The storage chamber 2h defined by 2d is partitioned into a first oil chamber 2i on the left side and a second oil chamber 2j on the right side, and the first and second oil chambers 2i and 2j have a viscous fluid OI. The point that is filled is different. 6 to 8, 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.

  The piston 12 shown in FIG. 6 is formed in a disc shape, contacts the inner surface of the peripheral wall 2c via a seal s provided integrally on the outer periphery thereof, and is rotatable with respect to the main body portion 2, and includes a storage chamber. It can slide in the left-right direction within 2h. The first oil chamber 2i defined by the piston 12 accommodates the left thrust bearing 7L and the left disc spring unit 8L, and the left disc spring unit 8L is disposed between the piston 12 and the left thrust bearing 7L. ing. The second oil chamber 2j defined by the piston 12 accommodates the right thrust bearing 7R and the right disc spring unit 8R. The right disc spring unit 8R is interposed between the piston 12 and the right thrust bearing 7R. Has been placed. The viscous fluid OI filled in the first and second oil chambers 2i and 2j is made of silicon oil.

  Further, the piston 12 is provided with a first pressure regulating valve 13 and a second pressure regulating valve 14. As shown in FIG. 7, each pressure regulating valve 13, 14 includes a valve body 13 a, 14 a and springs 13 b, 14 b. Each is composed of a combination. The first pressure regulating valve 13 is opened when the pressure of the viscous fluid OI in the first oil chamber 2i reaches a relatively low predetermined pressure, and causes the first and second oil chambers 2i and 2j to communicate with each other. The second pressure regulating valve 14 is opened when the pressure of the viscous fluid OI in the second oil chamber 2j reaches the predetermined pressure, and allows the second and first oil chambers 2j and 2i to communicate with each other.

  Although not shown, the mass damper 11 having the above configuration is connected to the upper beam BU and the lower beam BD of the building B in a brace shape, for example, like the mass damper 1 of the first embodiment.

  As the building B vibrates, a relative displacement occurs between the upper and lower beams BU and BD. As a result, when a tensile force acts on the mass damper 11, the rod 3 and the screw shaft 4a are moved as in the case of the first embodiment. The main body 2 moves to the left and right. Accordingly, the left disc spring unit 8L is pressed by the piston 12 integral with the rod 3 and the left thrust bearing 7L attached to the left side wall 2a of the main body 2, and the viscous fluid OI in the first oil chamber 2i is A nut 4c that is pressed by the piston 12 and screwed into the screw shaft 4a rotates together with the main body 2 with respect to the rod 3 and the screw shaft 4a. At that time, when the pressure of the viscous fluid OI in the first oil chamber 2i reaches a predetermined pressure due to the pressing by the piston 12, the first pressure regulating valve 13 is opened, so that the first and second oil chambers 2i, 2j are opened. A part of the viscous fluid OI in the first oil chamber 2i flows into the second oil chamber 2j.

  As described above, when a tensile force acts on the mass damper 11 with the vibration of the building B, the relative displacement between the upper and lower beams BU and BD is as follows: the rod 3, the piston 12, the left disc spring unit 8L, It is transmitted to the main body 2 through the thrust bearing 7L, the screw shaft 4a and the nut 4c in a state of being converted into a rotational motion, whereby the main body 2 which is also used as a rotating mass rotates. At that time, as the first pressure regulating valve 13 is opened, a part of the viscous fluid OI in the first oil chamber 2i flows into the second oil chamber 2j, whereby a viscous damping effect by the viscous fluid OI is obtained.

  On the other hand, when a compressive force is applied to the mass damper 11, the rod 3 and the screw shaft 4 a move to the right and left with respect to the main body 2, respectively. Accordingly, the right disc spring unit 8R is pressed by the piston 12 and the right thrust bearing 7R attached to the housing wall 2d of the main body 2, and the viscous fluid OI in the second oil chamber 2j is pressed by the piston 12. At the same time, the nut 4c rotates with the main body 2 relative to the rod 3 and the screw shaft 4a. At that time, when the pressure of the viscous fluid OI in the second oil chamber 2j reaches a predetermined pressure due to the pressing by the piston 12, the second pressure regulating valve 14 is opened, whereby the second and first oil chambers 2j, 2i are opened. A part of the viscous fluid OI in the second oil chamber 2j flows into the first oil chamber 2i.

  As described above, when a compressive force acts on the mass damper 11 with the vibration of the building B, the relative displacement between the upper and lower beams BU and BD is as follows: the rod 3, the piston 12, the right disc spring unit 8R, It is transmitted to the main body 2 through the thrust bearing 7R, the screw shaft 4a and the nut 4c in a state of being converted into a rotational motion, whereby the main body 2 rotates. At that time, as the second pressure regulating valve 14 is opened, a part of the viscous fluid OI in the second oil chamber 2j flows into the first oil chamber 2i, thereby obtaining a viscous damping effect by the viscous fluid OI.

  As is apparent from the operation of the mass damper 11 described above, in the mass damper 11, the main body 2 that is also used as a rotating mass and the left disc spring unit 8 </ b> L (right disc spring unit 8 </ b> R) are connected in series with each other. In addition, there is a relationship in which a viscous damping element VD made of a viscous fluid OI or the like is connected in parallel to the left disc spring unit 8L (right disc spring unit 8R). For this reason, the model diagram of the mass damper 11 is expressed as shown in FIG. 8, for example.

  As described above, in the mass damper 11, as in the mass damper 1 of the first embodiment, the additional vibration system can be configured by the main body 2 and the left disk spring unit 8L (the right disk spring unit 8R). Is set so as to tune (resonate) with the natural frequency of the structure (for example, the primary natural frequency) based on the fixed point theory. The setting method is performed in the same manner as in the first embodiment. Further, the damping coefficient of the viscous fluid OI is set based on the fixed point theory so as to minimize the peak of the response magnification curve by the optimum damping.

  As described above, according to the second embodiment, the main body 2 is arranged in a state in which the cylindrical peripheral wall 2c extending in the axial direction and the left portion of the main body 2 are spaced apart from each other in the axial direction. The wall 2a and the housing wall 2d are integrally provided. A storage chamber 2h is defined in the left part of the main body 2 by a peripheral wall 2c, a left side wall 2a, and a storage wall 2d. Each of the left side wall 2a and the storage wall 2d is inserted in an axial direction. Holes 2e and 2g are formed. The rod 3 is inserted into the insertion holes 2e and 2g, thereby supporting the main body 2 rotatably.

  The piston 12 integral with the rod 3 is provided in the accommodation chamber 2h so as to be rotatable and slidable in the axial direction, and the accommodation chamber 2h is divided into a first oil chamber 2i and a second oil chamber 2j. ing. The left and right thrust bearings 7L and 7R are provided on the left side wall 2a and the accommodation wall 2d, respectively, and are accommodated in the first and second oil chambers 2i and 2j, respectively. The left and right disc spring units 8L and 8R are 1 and the second oil chambers 2i and 2j, respectively. The first and second oil chambers 2i and 2j are filled with a viscous fluid OI, and the piston 12 is used to adjust the pressure of the viscous fluid OI in the first and second oil chambers 2i and 2j. In addition, there are provided first and second pressure regulating valves 13 and 14 for communicating the two oil chambers 2i and 2j with each other.

  As described above, the accommodating chamber 2h defined inside the left portion of the main body 2 is filled with the viscous fluid OI, and the piston 12 integral with the rod 3 is provided so as to be slidable in the axial direction. The pressure of the viscous fluid OI in the first and second oil chambers 2 i and 2 j defined by the piston 12 is adjusted by the first and second pressure regulating valves 13 and 14. Therefore, when the relative displacement between the upper and lower beams BU and BD is transmitted to the rod 3 and the screw shaft 4a, when the piston 12 slides in the housing chamber 2h, the first and second oil chambers 2i, Since the viscous fluid OI inside one of 2j is pressed by the piston 12, and the pressure is adjusted by the first and second pressure regulating valves 13, 14, the viscous damping effect by the viscous fluid OI can be further obtained. As a result, the vibration of the building B can be suppressed more appropriately. In addition, the effect by 1st Embodiment can be acquired similarly.

  In the first embodiment, the left and right thrust bearings 7L and 7R are provided so as to contact the inner diameter portions of the left and right disc spring units 8L and 8R. However, as shown in FIG. You may provide so that it may contact the outer diameter part of 8L and 8R. In that case, since the number of balls of the left and right thrust bearings 7L and 7R can be increased, it is possible to cope with a larger load in the left-right direction. The same applies to the second embodiment.

  In the first embodiment, the left thrust bearing 7L is provided on the left side wall 2a. However, the left thrust bearing 7L is provided at another appropriate position on the relative displacement transmission path including the left side wall 2a, the left disc spring unit 8L, and the flange 6. It may be provided. The same applies to the right thrust bearing 7 </ b> R, and it may be provided at another appropriate location on the relative displacement transmission path including the accommodation wall 2 d, the right disc spring unit 8 </ b> R, and the flange 6. For example, as shown in FIG. 15A, left and right thrust bearings 7L and 7R may be provided on the left and right surfaces of the flange 6, respectively. The same applies to the second embodiment, and the left and right thrust bearings 7L and 7R are replaced with the left side wall 2a and the housing wall 2d as shown in FIG. May be provided respectively. Alternatively, regarding the first and second embodiments, the left thrust bearing 7L may be provided between one of the plurality of disc springs 8a of the left disc spring unit 8L and the other one, and the right thrust bearing 7R may be provided to the right It may be provided between one of the plurality of disc springs 8a of the disc spring unit 8R and the other one.

  Next, a mass damper 21 according to a third embodiment of the present invention will be described with reference to FIGS. Compared with the first embodiment, the mass damper 21 is provided with a piston 22 integrally provided on the rod 3 instead of the flange 6, and a left piston 23L and a right piston 23R are provided on both the left and right sides of the piston 22, respectively. The first oil chamber 2k on the left side and the second oil chamber 2l on the right side are defined by the pistons 22, 23L, 23R, and the first and second oil chambers 2k, The difference is that 2l is filled with a viscous fluid OI. 10-12, the same code | symbol is attached | subjected about the same component as 1st Embodiment. Hereinafter, a description will be given focusing on differences from the first embodiment.

  The piston 22 shown in FIG. 10 is formed in a disk shape, contacts the inner surface of the peripheral wall 2c via a seal s provided on the outer periphery thereof, and is rotatable with respect to the main body 2 and is contained in the storage chamber 2h. Can be slid in the left-right direction. The left and right pistons 23L and 23R are formed in a donut plate shape, and are in contact with the inner surface of the peripheral wall 2c through a seal s provided on the outer periphery thereof, and are accommodated in the accommodation chamber 2h so as to be slidable in the left-right direction. Yes. Further, an insertion hole 23a penetrating in the left-right direction is coaxially provided at the center of each of the left and right pistons 23L, 23R. The rods 3 are inserted into the insertion holes 23a and 23a of the left and right pistons 23L and 23R through seals s, respectively. The left and right pistons 23L and 23R are rotatable with respect to the rod 3 and movable in the left and right direction. It is.

  In the storage chamber 2h, the first oil chamber 2k is partitioned by the piston 22 and the left piston 23L, and the second oil chamber 2l is partitioned by the piston 22 and the right piston 23R. The viscous fluid OI filled in the first and second oil chambers 2k and 2l is composed of silicon oil, as in the second embodiment. In the third embodiment, the left and right thrust bearings 7L, 7R are omitted, and the left disc spring unit 8L is disposed between the left piston 23L and the left side wall 2a, and the right disc spring unit 8R. Is disposed between the right piston 23R and the accommodating wall 2d.

  Further, the piston 22 is provided with a first relief valve 24 and a second relief valve 25. As shown in FIG. 11, each relief valve 24 and 25 is comprised by the combination of valve body 24a, 25a and spring 24b, 25b similarly to the 1st and 2nd pressure regulation valves 13 and 14 of 2nd Embodiment, respectively. Yes. The first relief valve 24 is opened when the pressure of the viscous fluid OI in the first oil chamber 2k reaches a relatively high predetermined upper limit pressure, and allows the first and second oil chambers 2k, 2l to communicate with each other. . The second relief valve 25 opens when the pressure of the viscous fluid OI in the second oil chamber 2l reaches the upper limit pressure, and allows the second and first oil chambers 2l and 2k to communicate with each other.

  Although not shown, the mass damper 21 having the above configuration is connected to the upper beam BU and the lower beam BD of the building B in a brace shape, for example, like the mass damper 1 of the first embodiment.

  As the building B vibrates, a relative displacement occurs between the upper and lower beams BU and BD. As a result, when a tensile force acts on the mass damper 21, the rod 3 and the screw shaft 4a are moved as in the case of the first embodiment. The main body 2 moves to the left and right. Accordingly, the viscous fluid OI in the first oil chamber 2k is pressed by the piston 22 integral with the rod 3 and the left piston 23L, and the left disc spring unit 8L is moved to the left piston 23L and the left side wall 2a of the main body 2. The nut 4c screwed with the screw shaft 4a and the main body 2 rotate with respect to the rod 3 and the screw shaft 4a. At that time, when the pressure of the viscous fluid OI in the first oil chamber 2k reaches the upper limit pressure due to the pressing by the piston 22 and the left piston 23L, the first relief valve 24 is opened, whereby the first and second oil chambers are opened. 2k and 2l communicate with each other, and a part of the viscous fluid OI in the first oil chamber 2k flows into the second oil chamber 2l.

  As described above, when a tensile force acts on the mass damper 21 with the vibration of the building B, the relative displacement between the upper and lower beams BU and BD is as follows: the rod 3, the piston 22, the viscous fluid OI, and the left piston 23L. Through the left disc spring unit 8L, the screw shaft 4a and the nut 4c, the rotation is transmitted to the main body 2 in a state of being converted into a rotational motion, whereby the main body 2 which is also used as a rotating mass rotates. At that time, when the first relief valve 24 is opened, a part of the viscous fluid OI in the first oil chamber 2k flows into the second oil chamber 2l, so that a viscous damping effect by the viscous fluid OI is obtained.

  On the other hand, when a compressive force acts on the mass damper 21, the rod 3 and the screw shaft 4 a move to the right and left with respect to the main body 2, respectively. Accordingly, the viscous fluid OI in the second oil chamber 21 is pressed by the piston 22 integral with the rod 3 and the right piston 23R, and the right disc spring unit 8R is moved to the right piston 23R and the housing wall 2d of the main body 2. The nut 4c rotates with respect to the rod 3 and the screw shaft 4a together with the main body 2. At this time, when the pressure of the viscous fluid OI in the second oil chamber 21 reaches the upper limit pressure by the piston 22 and the right piston 23R, the second relief valve 25 is opened, whereby the second and first oil chambers are opened. 2l and 2k communicate with each other, and a part of the viscous fluid OI in the second oil chamber 2l flows into the first oil chamber 2k.

  As described above, when a compressive force acts on the mass damper 21 with the vibration of the building B, the relative displacement between the upper and lower beams BU and BD is as follows: the rod 3, the piston 22, the viscous fluid OI, and the right piston 23R. Through the right disc spring unit 8R, the screw shaft 4a and the nut 4c, it is transmitted to the main body 2 in a state converted to a rotational motion, whereby the main body 2 rotates. At this time, as the second relief valve 25 is opened, a part of the viscous fluid OI in the second oil chamber 2l flows into the first oil chamber 2k, thereby obtaining a viscous damping effect by the viscous fluid OI.

  As is apparent from the operation of the mass damper 21 described above, in the mass damper 21, the main body 2 that is also used as a rotating mass and the left disc spring unit 8L (right disc spring unit 8R) are connected in series with each other. . Further, when the pressure of the viscous fluid OI in the first and second oil chambers 2k and 2l is lower than the upper limit pressure, the first and second relief valves 24 and 25 are held in the closed state, thereby causing the viscous fluid. Since the OI does not flow, the viscous damping effect by the viscous fluid OI cannot be obtained. For this reason, in this case, a model diagram of the mass damper 21 is expressed as shown in FIG.

  On the other hand, when the pressure of the viscous fluid OI in the first and second oil chambers 2k and 2l is equal to or higher than the upper limit pressure, the first and second relief valves 24 and 25 are opened, and the viscous fluid OI flows. The viscous damping effect by the viscous fluid OI can be obtained. In this case, as is apparent from the above-described operation, the viscous damping element VD made of the viscous fluid OI or the like is connected in series to the left disc spring unit 8L (right disc spring unit 8R). The model diagram 21 is represented as shown in FIG.

  As described above, in the mass damper 21, as in the mass damper 1 of the first embodiment, the additional vibration system can be configured by the main body 2 and the left disk spring unit 8L (the right disk spring unit 8R). Is set so as to tune (resonate) with the natural frequency of the structure (for example, the primary natural frequency) based on the fixed point theory. The setting method is performed in the same manner as in the first embodiment. Further, the damping coefficient of the viscous fluid OI may be set based on the fixed point theory so as to minimize the peak of the response magnification curve by the optimum damping.

  As described above, according to the third embodiment, the cylindrical main body 2 is also used as a rotating mass, and the screw shaft 4a is a part of the right portion of the main body 2 that is movable in the axial direction. And coaxially. The screw shaft 4a is connected to the lower beam BD and extends in the axial direction. A nut 4c attached to the right part of the main body is screwed onto the screw shaft 4a via a ball 4b. The rod 3 is accommodated in the left part of the main body 2 partially and coaxially so as to be movable in the axial direction. The rod 3 is connected to the upper beam BU, extends in the axial direction, and rotatably supports the main body 2. The rod 3 is integrally provided with a piston 22, and the piston 22 is accommodated in the left portion of the main body 2 so as to be rotatable and slidable in the axial direction.

  The left part of the main body 2 accommodates left and right disc spring units 8L and 8R and left and right pistons 23L and 23R. These left and right disc spring units 8L and 8R are composed of a plurality of disc springs 8a stacked in the axial direction, and are arranged on both the left and right sides of the piston 22, and the rod 3 is inserted therein. The left and right pistons 23L and 23R are arranged between the piston 22 and the left disc spring unit 8L and between the piston 22 and the right disc spring unit 8R, respectively, and the inside of the left portion of the main body 2 is axially arranged. It can slide, can move in the axial direction with respect to the rod 3, and can rotate with respect to the rod 3. In addition, a first oil chamber 2k and a second oil chamber 21 are defined in the left portion of the main body 2 between the piston 22, the left piston 23L, and the right piston 23R. The first and second oil chambers 2k and 2l are filled with a viscous fluid OI.

  The relative displacement between the upper and lower beams BU, BD generated by the vibration of the building B is transmitted to the screw shaft 4a and the rod 3, and further, the nut 4c, the piston 22, the viscous fluid OI, the piston 23L (23R), And it is transmitted to the main-body part 2 in the state converted into rotational motion via the disc spring unit 8L (8R). Thereby, the main-body part 2 used also as a rotation mass rotates, and the rotation inertial mass effect by the main-body part 2 is acquired, Therefore The vibration of the building B can be suppressed appropriately. At that time, the disc spring unit 8L (8R) is pressed by the viscous fluid OI, the piston 23L (23R) and the main body 2 and exhibits its rigidity, so that it is added by the main body 2 and the disc spring unit 8L (8R). A vibration system can be configured. This makes it possible to connect the mass damper 21 to the upper and lower beams BU and BD without using an attachment member having a spring function such as a steel material that is generally used to form an additional vibration system together with the rotating mass. . In this case, the movement of the rod 3 and the piston 22 with respect to the screw shaft 4a is transmitted to the main body 2 via the viscous fluid OI that can be sheared in the circumferential direction, and via the viscous fluid OI as the piston 22 moves. Since the piston 23 </ b> L (23 </ b> R) pressed in this manner is rotatable with respect to the rod 3, the main body 2 can be appropriately rotated with respect to the rod 3.

  Further, as is apparent from the above description, the mass damper 21 has the same function as the conventional mass damper described above, as the mass damper 1 according to the first embodiment, and serves as an elastic body for constituting the additional vibration system. The disc spring unit 8L (8R) and the main body 2 (rotary mass) can be connected in series with each other. On the other hand, unlike the conventional mass damper, a complicated configuration such as an end cylinder, a lid, and a plurality of keys is not required, so that the mass damper 21 can be configured relatively easily. In this case, since the main body 2 and the rotary mass are configured by members that are common to each other, the number of parts can be reduced accordingly, and thus the manufacturing cost can be reduced, and the mass damper 21 can be configured more simply. can do.

  Further, unlike the mass damper 1 according to the first embodiment, unlike the conventional mass damper, the main body 2 and the rotary mass are formed of a common member, and the rotary mass is not accommodated in the main body 2. The rotational inertial mass of can be easily adjusted. For the same reason, in order to obtain a large rotational inertial mass effect of the rotating mass, even if the area of the surface orthogonal to the axial direction is increased, the area of the surface orthogonal to the axial direction of the main body 2 differs from the conventional mass damper. Therefore, the mass damper 21 can be downsized as a whole.

  Further, in the mass damper 21, as the relative displacement between the upper and lower beams BU and BD is transmitted to the screw shaft 4a and the rod 3, the viscous fluid OI in the first and second oil chambers 2k and 2l is moved to the piston. 22 and left and right pistons 23L and 23R. For this reason, since the pressure of the viscous fluid OI becomes a load and acts on the rod 3 and the screw shaft 4a in the axial direction, this load (hereinafter referred to as “axial load”) increases as the pressure of the viscous fluid OI increases. . Since the piston 22 is provided with the first and second relief valves 24 and 25 for preventing the pressure of the viscous fluid OI in the first and second oil chambers 2k and 2l from being excessive, excessive axial load is provided. Can be prevented. Further, the first and second relief valves 24, 25 allow the first and second oil chambers 2k, 2l to communicate with each other, thereby further obtaining a viscous damping effect by the fluid.

  In the third embodiment, the left and right thrust bearings 7L and 7R are omitted, but it is needless to say that both 7L and 7R may be provided as shown in FIG. In this case, as shown in FIG. 9 described above, the left and right thrust bearings 7L and 7R may be provided so as to contact the outer diameter portions of the left and right disc spring units 8L and 8R. In addition, the variation regarding the left and right thrust bearings 7L and 7R described with reference to FIG. 15 can be appropriately employed. In the third embodiment, the left and right pistons 23L and 23R are provided so as to be rotatable with respect to the rod 3. However, the left and right pistons 23L and 23R may be provided so as not to rotate with respect to the rod 3 and to be rotatable with respect to the main body 2. 3 and the main body 2 may be provided so as to be rotatable. Furthermore, in the third embodiment, the first and second relief valves 24 and 25 are provided, but may be omitted.

  FIG. 14 shows a mass damper 31 according to the fourth embodiment of the present invention. The mass damper 31 is different from the first embodiment only in that an adjustment mass 32 for adjusting the rotational inertial mass is attached to the main body 2. In FIG. 14, 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.

  The adjustment mass 32 is made of a material having a relatively large specific gravity, for example, iron, like the main body 2, is formed in a ring shape, and is coaxially provided outside the main body 2. The adjustment mass 32 is formed with a plurality of insertion holes 32a (only two are shown) penetrating in the radial direction. Bolts 33 are inserted into the respective insertion holes 32 a from the outside, and the bolts 33 are screwed into the peripheral wall 2 c of the main body 2. Thereby, the adjustment mass 32 is attached to the main body 2.

  As described above, according to the fourth embodiment, the adjustment mass 32 for adjusting the rotational inertial mass of the main body 2 is attached to the main body 2, so that the rotational inertial mass can be adjusted more easily. can do.

  In the fourth embodiment, as in the first embodiment, the left and right thrust bearings 7L and 7R are provided in contact with the inner diameter portions of the left and right disc spring units 8L and 8R. As shown, you may provide so that it may contact the outer-diameter part of a left and right disc spring unit. In the fourth embodiment, as in the first embodiment, the left and right thrust bearings 7L and 7R are provided on the left side wall 2a and the accommodating wall 2d, respectively, but as shown in FIG. You may provide in the left surface and the right surface of the flange 6, respectively. Alternatively, the left thrust bearing 7L may be provided between one of the plurality of disc springs 8a of the left disc spring unit 8L and the other one, and the right thrust bearing 7R is provided of the plurality of disc springs of the right disc spring unit 8R. You may provide between one of 8a and another one. Furthermore, in 4th Embodiment, although the structure which provided the mass 34 for adjustment in the mass damper 1 by 1st Embodiment is employ | adopted as the mass damper 31, it is for adjustment to the mass dampers 11 and 21 by 2nd or 3rd embodiment. Of course, a configuration in which the mass 32 is provided may be adopted. Also in this case, the above-described variations regarding the left and right thrust bearings 7L and 7R can be appropriately employed.

  Next, a mass damper 41 according to a fifth embodiment of the present invention will be described with reference to FIG. Compared to the first embodiment, the mass damper 41 is provided with a rod 3 in which a pair of left and right flanges 6L and 6R are integrally provided instead of the flange 6 described above, and is integrally provided on the peripheral wall 2c. The main difference is that the donut-shaped engagement wall 2m is arranged between the left and right flanges 6L, 6R. In FIG. 16, 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.

  As shown in FIG. 16, the engagement wall 2m is formed with an insertion hole 2n penetrating in the left-right direction, and the insertion hole 2n is arranged coaxially with the peripheral wall 2c. The rod 3 is inserted into the insertion hole 2n via the sliding material 5 and extends in the left-right direction. The left thrust bearing 7L is provided on the right surface of the left flange 6L, and the right thrust bearing 7R is provided on the left surface of the right flange 6R. The left disc spring unit 8L is disposed between the left thrust bearing 7L and the engagement wall 2m, and the right disc spring unit 8R is disposed between the right thrust bearing 7R and the engagement wall 2m.

  Although not shown, the mass damper 41 having the above configuration is connected to the upper beam BU and the lower beam BD of the building B in a brace shape, for example, like the mass damper 1 of the first embodiment.

  When relative displacement occurs between the upper and lower beams BU and BD along with the vibration of the building B, and a compressive force acts on the mass damper 41, the rod 3 and the screw shaft 4a are moved to the main body as in the first embodiment. Move to the right and left with respect to part 2 respectively. Accordingly, the left disc spring unit 8L is pressed by the left thrust bearing 7L provided on the left flange 6L integral with the rod 3 and the engagement wall 2m of the main body 2 and screwed into the screw shaft 4a. The nut 4c rotates together with the main body 2 with respect to the rod 3 and the screw shaft 4a. Thus, when a compressive force acts on the mass damper 41 with the vibration of the building B, the relative displacement between the upper and lower beams BU, BD is as follows: rod 3, left flange 6L, left thrust bearing 7L, left plate. It is transmitted to the main body 2 through the spring unit 8L, the screw shaft 4a and the nut 4c in a state of being converted into a rotational motion, whereby the main body 2 which is also used as a rotating mass rotates.

  On the other hand, when a tensile force is applied to the mass damper 41, the rod 3 and the screw shaft 4a move to the left and right with respect to the main body 2 as in the first embodiment. Accordingly, the right disc spring unit 8R is pressed by the right thrust bearing 7R provided on the right flange 6R integral with the rod 3 and the engagement wall 2m of the main body 2 and the nut 4c is connected to the main body 2 Together with the rod 3 and the screw shaft 4a. As described above, when a tensile force acts on the mass damper 41 with the vibration of the building B, the relative displacement between the upper and lower beams BU and BD is as follows: the rod 3, the right flange 6R, the right thrust bearing 7R, and the right plate. It is transmitted to the main body 2 through the spring unit 8R, the screw shaft 4a and the nut 4c in a state of being converted into rotational motion, whereby the main body 2 rotates.

  As is apparent from the operation of the mass damper 41 described above, in the mass damper 41, as in the first embodiment, the main body 2 that is also used as a rotating mass and the left disc spring unit 8L (right disc spring unit 8R) are connected in series. Is linked to For this reason, the model diagram of the mass damper 41 is expressed as shown in FIG. 3, for example.

  As mentioned above, according to 5th Embodiment, the effect mentioned above by 1st Embodiment can be acquired similarly.

  In the fifth embodiment, as in the first embodiment, the left and right thrust bearings 7L and 7R are provided so as to contact the inner diameter portions of the left and right disc spring units 8L and 8R. As shown, you may provide so that the outer diameter part of the left and right disc spring units 8L and 8R may be contacted.

  Further, in the fifth embodiment, the left thrust bearing 7L is provided on the left flange 6L. However, another appropriate transmission path on the relative displacement transmission path including the left flange 6L, the left disc spring unit 8L, and the engagement wall 2m is used. You may provide in a site | part. The same applies to the right thrust bearing 7R, and the right thrust bearing 7R is provided at another appropriate portion on the relative displacement transmission path including the right flange 6R, the right disc spring unit 8R, and the engagement wall 2m. May be. For example, the left and right thrust bearings 7L and 7R may be provided on the left surface and the right surface of the engagement wall 2m, respectively, or between one of the plurality of disc springs 8a of the left disc spring unit 8L and the other one, and The right disc spring unit 8R may be provided between one of the plurality of disc springs 8a and the other one.

  Furthermore, regarding the fifth embodiment, instead of the left and right flanges 6L and 6R, the left and right pistons configured in the same manner as the piston 12 of the second embodiment are used so as to obtain the above-described viscous damping effect by the viscous fluid OI. It may be configured. Alternatively, a piston configured in the same manner as the piston 12 is provided at the right end portion of the rod or the left end portion of the screw shaft, and the fluid chamber containing the piston and the viscous fluid is defined in the main body portion, whereby the viscous fluid You may comprise so that the viscous damping effect by may be acquired. Of course, regarding the fifth embodiment, a configuration in which the adjustment mass 32 of the fourth embodiment is provided may be adopted.

  Next, a mass damper 51 according to a sixth embodiment of the present invention will be described with reference to FIG. The mass damper 51 is mainly different from the first embodiment in the configuration related to the disc spring unit 8. In FIG. 17, 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.

  As shown in FIG. 17, the left side wall 2o provided integrally with the left end portion of the peripheral wall 2c of the main body 2 is formed in a donut plate shape like the left side wall 2a of the first embodiment, and the left side wall 2o Are provided with an insertion hole 2p penetrating in the left-right direction and a recess 2q continuous to the insertion hole 2p. The insertion hole 2p and the recess 2q are arranged coaxially with the peripheral wall 2c. The recess 2q opens to the right and has a larger diameter than a left flange 52L described later. In addition, a donut plate-shaped accommodation wall 2r is integrally provided on the left portion of the peripheral wall 2c. Similarly to the left side wall 2o, the accommodation wall 2r has an insertion hole 2s penetrating in the left-right direction and an insertion hole 2s. A recess 2t that is continuous with the first and second recesses is provided. The insertion hole 2s and the recess 2t are arranged coaxially with the peripheral wall 2c. The recess 2t opens to the left and has a larger diameter than a right flange 52R described later. The rod 3 is inserted into the insertion holes 2p and 2s through the sliding members 5 and 5 and extends in the left-right direction, and supports the main body 2 rotatably like the first embodiment.

  The housing chamber 2u defined by the peripheral wall 2c, the left side wall 2o, and the housing wall 2r includes a pair of left and right thrust bearings 7L and 7R, flanges 52L and 52R, plates 53L and 53R, and a plurality of disc springs 8a. The disc spring unit 8 stacked in the direction is accommodated. The left and right thrust bearings 7L and 7R have larger inner diameters than the left and right flanges 52L and 52R, are provided on the left side wall 2o and the receiving wall 2r, and are arranged coaxially with the peripheral wall 2c.

  The left and right flanges 52L and 52R are formed in a cylindrical shape having a larger diameter than the rod 3, and are provided integrally with the rod 3. The left and right flanges 52L and 52R are movable in the left and right directions together with the rod 3 in the housing chamber 2u. They are arranged in the direction spaced apart from each other. When the rod 3 is in the neutral position shown in FIG. 17, the left and right flanges 52L and 52R are positioned inside the left and right thrust bearings 7L and 7R, respectively, and the right surfaces of the left flange 52L and the left thrust bearing 7L are mutually connected. The left surfaces of the right flange 52R and the right thrust bearing 7R are flush with each other.

  The left and right plates 53L and 53R are formed in a donut plate shape, and the rod 3 is inserted into a radial insertion hole (not shown) penetrating in the left-right direction. On the other hand, it can move in the left-right direction. The diameters of the insertion holes of the left and right plates 53L and 53R are smaller than the diameters of the left and right flanges 52L and 52R. The left and right plates 53L and 53R are disposed between the left and right flanges 52L and 52R. When the rod 3 is in the neutral position, the left surface of the left plate 53L is the left flange 52L and the left thrust bearing 7L. The right surface of the right plate 53R is in contact with the right flange 52R and the left surface of the right thrust bearing 7R. The disc spring unit 8 is disposed between the left and right plates 53L and 53R, and the rod 3 is inserted into the center hole of the plurality of disc springs 8a.

  Although not shown, the mass damper 51 having the above configuration is connected to the upper beam BU and the lower beam BD of the building B in a brace shape, for example, as in the mass damper 1 of the first embodiment.

  When the building B vibrates, a relative displacement occurs between the upper and lower beams BU and BD. When a compressive force is applied to the mass damper 51, the rod 3 and the screw shaft 4a are moved to the right with respect to the main body 2. And move to the left respectively. Accordingly, as shown in FIG. 18, the left flange 52L integrated with the rod 3 presses the left plate 53L to the right, and the pressing force of the left flange 52L is changed from the left plate 53L to the disc spring unit 8 and the right plate 53R. And the nut 4c, which is transmitted to the receiving wall 2r via the right thrust bearing 7R and is compressed by the disc spring unit 8 and screwed into the screw shaft 4a, together with the main body 2 and the rod 3 and screw shaft 4a. Rotate against. Further, the right flange 52R is separated from the right plate 53R to the right, and the movement of the right flange 52R is ensured by the recess 2t of the housing wall 2r.

  As described above, when a compressive force is applied to the mass damper 51 as the building B vibrates, the relative displacement between the upper and lower beams BU and BD is as follows: the rod 3, the left flange 52L, the left plate 53L, and the disc spring. Via the unit 8, the right plate 53R, the right thrust bearing 7R, the screw shaft 4a, and the nut 4c, it is transmitted to the main body 2 in a state of being converted into a rotational motion, whereby the main body 2 that is also used as a rotating mass is obtained. Rotate.

  On the other hand, when a tensile force acts on the mass damper 51, the rod 3 and the screw shaft 4 a move to the left and right with respect to the main body 2, respectively. Accordingly, the right flange 52R integrated with the rod 3 presses the right plate 53R to the left, and the pressing force of the right flange 52R is transmitted from the right plate 53R to the disc spring unit 8, the left plate 53L, and the left thrust bearing 7L. The nut 4c, which is transmitted to the left side wall 2o and is compressed by the disc spring unit 8 and is screwed into the screw shaft 4a, rotates together with the main body 2 with respect to the rod 3 and the screw shaft 4a. Further, the left flange 52L is separated from the left plate 53L to the left, and the movement of the left flange 52L is secured by the recess 2q of the left side wall 2o.

  As described above, when a tensile force acts on the mass damper 51 with the vibration of the building B, the relative displacement between the upper and lower beams BU and BD is as follows: the rod 3, the right flange 52R, the right plate 53R, and the disc spring. It is transmitted to the main body 2 through the unit 8, the left plate 53L, the left thrust bearing 7L, the screw shaft 4a and the nut 4c in a state of being converted into a rotational motion, whereby the main body 2 rotates.

  As is apparent from the operation of the mass damper 51, as in the first embodiment, in the mass damper 51, the main body 2 that is also used as a rotating mass and the disc spring unit 8 are connected in series with each other. For this reason, the model diagram of the mass damper 51 is represented in the same manner as FIG. 3 described above, for example.

  Thus, in the mass damper 51, an additional vibration system can be constituted by the main body 2 and the disc spring unit 8, and the natural frequency of the additional vibration system is determined based on the fixed point theory (the natural frequency ( For example, the frequency is set so as to be tuned (resonated) with the first-order natural frequency. The natural frequency f ′ of the additional vibration system is expressed by f ′ = sqrt {K ′ / M} / (2π) using the rotational inertia mass M of the main body 2 and the rigidity K ′ of the disc spring unit 8. The natural frequency f ′ of the additional vibration system is set by adjusting the rotational inertia mass M of the main body 2 and the rigidity K ′ of the disc spring unit 8. In this case, the adjustment of the rotational inertia mass M of the main body 2 and the adjustment of the rigidity K ′ of the disc spring unit 8 are performed in the same manner as in the first embodiment.

  As described above, according to the sixth embodiment, as in the first embodiment, the cylindrical main body 2 is also used as a rotating mass, and the screw shaft 4a is provided on the right side of the main body 2. It is accommodated partially and coaxially so as to be movable in the axial direction. The screw shaft 4a is connected to the lower beam BD and extends in the axial direction. Moreover, the nut 4c attached to the right side wall 2b of the main-body part 2 is screwingly engaged with the screw shaft 4a via the ball 4b. The rod 3 is accommodated in the left part of the main body 2 partially and coaxially so as to be movable in the axial direction. The rod 3 is connected to the upper beam BU, extends in the axial direction, and rotatably supports the main body 2.

  The rod 3 is integrally provided with a pair of left and right flanges 52L and 52R, and these flanges 52L and 52R are movable in the axial direction between the left side wall 2o of the main body 2 and the receiving wall 2r. Are arranged in a state of being spaced apart from each other in the axial direction. A disc spring unit 8 is disposed between the pair of flanges 52L and 52R. Between the left flange 52L and the disc spring unit 8, and between the right flange 52R and the disc spring unit 8, left and right plates are arranged. 53L and 53R are respectively arranged. These plates 53L and 53R are configured to be movable in the axial direction with respect to the main body 2 and the rod 3, and as the rod 3 moves in the axial direction with respect to the main body 2, the flanges 52L (52R ) And the pressing force of the flange 52L (52R) is transmitted to one of the left side wall 2o and the accommodation wall 2r via the disc spring unit 8.

  The relative displacement between the upper and lower beams BU and BD generated by the vibration of the structure is as follows: screw shaft 4a, nut 4c, rod 3, flange 52L (52R), disc spring unit 8, plate 53L (53R), and It is transmitted to the main body 2 through the accommodation wall 2r (left side wall 2o) in a state converted into a rotational motion. As a result, as in the first embodiment, the main body 2 that is also used as a rotating mass rotates with respect to the rod 3, and a rotational inertial mass effect by the rotating mass is obtained, so that vibration of the structure is appropriately suppressed. Can do. At this time, as is apparent from the operations of the flange 52L (52R), the disc spring unit 8 and the plate 53L (53R) accompanying the movement of the rod 3, the disc spring unit 8 includes the flange 52L (52R), the plate 53L, Since it is pressed by 53R and the accommodation wall 2r (left side wall 2o) and exhibits its rigidity, the main body 2 and the disc spring unit 8 can constitute an additional vibration system.

  Thereby, it becomes possible to connect the mass damper 51 to the upper and lower beams BU and BD without using an attachment member having a spring function such as a steel material generally used for constituting the additional vibration system together with the rotating mass. . In this case, along with transmission of relative displacement between the upper and lower beams BU, BD to the main body 2, the flange 52L (52R), the disc spring unit 8, the plates 53L, 53R, and the receiving wall 2r (left side wall 2o) are formed. An axial pressing force (axial load) is generated on the relative displacement transmission path. According to the sixth embodiment, since the thrust bearing 7L (7R) is provided on the transmission path, the main body 2 can be appropriately rotated with respect to the rod 3.

  Further, as is apparent from the above description, the mass damper 51 has the same function as the above-described conventional mass damper, similarly to the mass damper 1 according to the first embodiment, and the main body 2 for constituting the additional vibration system. And the disc spring unit 8 can be connected in series with each other. On the other hand, unlike the conventional mass damper, a complicated configuration such as an end cylinder, a lid, and a plurality of keys is not required, so that the mass damper 51 can be configured relatively easily. In this case, since the main body 2 and the rotating mass are configured by members that are common to each other, the number of parts can be reduced accordingly, and thus the manufacturing cost can be reduced, and the mass damper 51 can be configured more simply. can do. In addition, the effect by 1st Embodiment can be acquired similarly.

  In the sixth embodiment, the left thrust bearing 7L is provided on the left side wall 2o. However, the other member on the relative displacement transmission path including the left flange 52L, the left plate 53L, the disc spring unit 8, and the right plate 53R is provided. You may provide in an appropriate site | part. The same applies to the right thrust bearing 7R, and the right thrust bearing 7R is connected to another appropriate portion on the relative displacement transmission path including the right flange 52R, the right plate 53R, the disc spring unit 8, and the left plate 53L. May be provided.

  For example, the left thrust bearing 7L may be provided between the left flange 52L and the left plate 53L, and the right thrust bearing 7R may be provided between the right flange 52R and the right plate 53L. In this case, the left and right plates 53L and 53R are in contact with the left side wall 2o and the accommodation wall 2r, respectively. Incidentally, when the thrust bearing 7L (7R) is provided on the transmission path including the left plate 53L, the disc spring unit 8 and the right plate 53R among the transmission paths, a single thrust bearing may be provided. . In any of these cases, the left and right plates 53L and 53R are provided to be rotatable with respect to the rod 3.

  Further, regarding the sixth embodiment, instead of the left and right plates 53L and 53R, the left and right pistons configured in the same manner as the piston 12 of the second embodiment are used so as to obtain the above-described viscous damping effect by the viscous fluid OI. It may be configured. However, unlike the piston 12, the piston in this case is provided so as to be movable in the axial direction with respect to the rod. Alternatively, a piston configured in the same manner as the piston 12 is provided at the right end portion of the rod or the left end portion of the screw shaft, and the fluid chamber containing the piston and the viscous fluid is defined in the main body portion, whereby the viscous fluid You may comprise so that the viscous damping effect by may be acquired. Of course, regarding the sixth embodiment, a configuration in which the adjustment mass 32 of the fourth embodiment is provided may be adopted.

  Furthermore, in the sixth embodiment, the left and right flanges 52L and 52R as the pair of pressing portions in the present invention are disposed between the left side wall 2o and the accommodating wall 2r, but extend in the axial direction (left and right direction). These may be inserted into the insertion holes of the left side wall and the accommodation wall, respectively, and may be protruded from the left side wall and the accommodation wall, respectively.

  The present invention is not limited to the first to sixth embodiments described below (hereinafter collectively referred to as “embodiments”), and can be implemented in various modes. For example, in the first to fifth embodiments, the compression force is not applied to the left and right disc spring units 8L and 8R in advance, but may be applied. In this case, the rigidity of both the left and right disc spring units is exhibited until the axial reaction force (hereinafter referred to as “damper reaction force”) acting on the left and right disc spring units from the main body reaches this compression force. After reaching the compression force, one of the left and right disc spring units is extended and the compression force is released, so that only the other rigidity of the left and right disc spring units is exhibited.

  That is, in this case, the entire left and right disc spring units have bilinear rigidity characteristics. For this reason, for example, when the rigidity of both the left and right disc spring units is exerted, the rotational inertia mass of the main body and the left and right sides of the main body are adjusted so that the natural frequency of the additional vibration system is synchronized with the natural frequency of the structure. By adjusting the rigidity of the disc spring unit, when the relative displacement input to the rod and the screw shaft increases, the natural frequency of the additional vibration system will not synchronize with the natural frequency of the structure. It is possible to prevent the shaft load acting on the screw shaft from becoming excessive. In this case, as the compressive force applied to the left and right disc spring units increases, the left and right disc spring units until the relative displacement input to the rod and the screw shaft increases, that is, until the damper reaction force increases. The rigidity of both is demonstrated.

  In the embodiment, the sliding material 5 is provided, but it is needless to say that the sliding material 5 may be omitted. Furthermore, in the second and third embodiments, the viscous fluid OI made of silicon oil is used, but other appropriate fluids may be used. In the embodiment, the main body 2 and the rotary mass are configured by members common to each other, but may be configured by separate members. In this case, by providing the rotating mass integrally on the outside of the main body, the above-described effects such as easy adjustment of the rotating inertia mass of the rotating mass can be obtained. Further, the rotary mass may be integrally provided inside the main body, and the present invention does not exclude such a configuration.

  Furthermore, in the embodiment, the cross section orthogonal to the axial direction of the main body 2 is circular, but may be square. Moreover, in 1st and 4th-6th embodiment, although the connection part in this invention is comprised with the surrounding wall 2c, when comprising the main-body part 2 and a rotation mass with a mutually separate member as mentioned above, The connecting portion may be configured by a plurality of bolts extending in the axial direction and arranged in the circumferential direction, and the left and right side walls 2a, 2b and the like may be integrally provided on these bolts. Furthermore, in the embodiment, the elastic body in the present invention is the disc spring units 8L, 8R, 8, but may be a coil spring or rubber. In the embodiment, one mass damper 1, 11, 21, 31, 41, 51 according to the present invention is provided in a brace shape on the upper and lower beams BU, BD. In order to suppress the displacement in the direction, it may be provided so as to extend in the vertical direction, or two mass dampers according to the present invention may be provided in the upper and lower beams in a V shape or an inverted V shape.

  Further, in the embodiment, the upper and lower beams BU and BD are respectively used as the first and second parts in the present invention to suppress the interlayer displacement between the two layers, but other appropriate parts may be adopted. Good. For example, as the first and second parts, upper and lower beams provided with one or more beams between each other may be adopted to suppress interlayer displacement between three or more layers, or building B You may employ | adopt each the foundation and beam which erected. In the embodiment, the mass dampers 1, 11, 21, 31, 41, 51 are connected to the beams BU and BD extending in the left-right direction, thereby suppressing left-right displacement due to vibration of the building B. By connecting to a beam extending in the direction, displacement in the front-rear direction due to vibration of the building may be suppressed. Furthermore, although embodiment is the example which applied the mass damper 1, 11, 21, 31, 41, 51 by this invention to the building B, this invention is applied to other suitable structures, for example, a steel tower, a bridge, etc. Is possible. In addition, it is possible to appropriately change the detailed configuration within the scope of the gist of the present invention.

B Building (structure)
BD Lower beam (first part)
BU upper beam (second part)
1 Mass damper 2 Main body (rotating mass)
2a Left side wall (a pair of wall portions, a pair of first engaging portions)
2c Perimeter wall (connecting part)
2d housing wall (a pair of wall portions, a pair of first engaging portions)
2e Insertion hole 2g Insertion hole 2h Storage chamber (fluid chamber)
3 Rod (support part)
4a Screw shaft 4b Ball 4c Nut 6 Flange (second engaging portion)
7L left thrust bearing (a pair of thrust bearings)
7R Right thrust bearing (a pair of thrust bearings)
8L left disc spring unit (a pair of disc spring units, a pair of elastic bodies)
8R right disc spring unit (a pair of disc spring units, a pair of elastic bodies)
8a Belleville spring 11 Mass damper 2i 1st oil chamber (1st fluid chamber)
2j Second oil chamber (second fluid chamber)
12 Piston (flange)
13 First pressure regulating valve (pressure regulating valve)
14 Second pressure regulating valve (pressure regulating valve)
OI viscous fluid (fluid)
21 Mass damper 2k 1st oil chamber (1st fluid chamber)
2l Second oil chamber (second fluid chamber)
22 Piston (Rod Piston)
23L Left piston (a pair of pistons)
23R Right piston (a pair of pistons)
24 First relief valve (Relief valve)
25 Second relief valve (Relief valve)
31 Mass damper 32 Adjustment mass 41 Mass damper 6L Left flange (a pair of first engaging portions)
6R Right flange (a pair of first engaging parts)
2m engagement wall (second engagement part)
51 Mass damper 2o Left side wall (a pair of walls)
2r accommodation wall (a pair of walls)
8 Belleville spring unit (elastic body)
52L left flange (a pair of pressing parts)
52R Right flange (a pair of pressing parts)
53L Left plate (a pair of transmission parts)
53R Right plate (a pair of transmission parts)

Claims (9)

A mass damper is provided between the first part and the second part in the system including the structure to suppress vibration of the structure,
A tubular body,
A rotating mass provided integrally with the main body,
A screw shaft that is connected to the first part and extends in the axial direction of the main body part, and is partially and coaxially accommodated in one axial part of the main body part so as to be movable in the axial direction. When,
A screw that is screwed to the screw shaft via a ball, and a nut attached to the one part of the main body,
It is connected to the second part, extends in the axial direction, and is accommodated partially and coaxially in the other part of the main body part in the axial direction so as to be movable in the axial direction, and rotates the main body part A supporting rod, and
A flange provided integrally with the rod, and accommodated in the other part of the main body so as to be movable in the axial direction;
A pair of thrust bearings housed in the other part of the main body, provided coaxially with the main body, and disposed on both sides of the flange in the axial direction;
A plurality of disc springs stacked in the axial direction, housed in the other part of the main body, and inserted with the rod, between the flange and one of the pair of thrust bearings, and A pair of disc spring units respectively disposed between the flange and the other of the pair of thrust bearings,
Relative displacement between the first part and the second part generated by the vibration of the structure is transferred via the screw shaft, the nut, the rod, the flange, the disc spring unit, and the thrust bearing. , Transmitted to the main body in a state converted into a rotational motion, whereby the main body and the rotary mass rotate with respect to the rod, and the disc spring unit moves in the axial direction at the flange and the main body. A mass damper characterized by being pressed by The main body portion integrally includes a cylindrical peripheral wall extending in the axial direction and a pair of wall portions arranged at intervals on the other portion of the main body portion in the axial direction. And
A fluid chamber is defined in the other portion of the main body by the pair of wall portions and the peripheral wall, and an insertion hole penetrating in the axial direction is formed in each of the pair of wall portions. And
The rod is rotatably inserted into the insertion hole to support the main body,
The flange is provided in the fluid chamber so as to be rotatable and slidable in the axial direction, and the fluid chamber is divided into a first fluid chamber and a second fluid chamber,
The pair of thrust bearings are respectively provided in the pair of wall portions, and are respectively accommodated in the first and second fluid chambers,
The pair of disc spring units are accommodated in the first and second fluid chambers, respectively.
A viscous fluid filled in the first and second fluid chambers;
And a pressure regulating valve provided on the flange and configured to allow the first and second fluid chambers to communicate with each other in order to adjust the pressure of the viscous fluid in the first and second fluid chambers. The mass damper according to claim 1. A mass damper is provided between the first part and the second part in the system including the structure to suppress vibration of the structure,
A tubular body,
A rotating mass provided integrally with the main body,
A screw shaft that is connected to the first part and extends in the axial direction of the main body part, and is partially and coaxially accommodated in one axial part of the main body part so as to be movable in the axial direction. When,
A screw that is screwed to the screw shaft via a ball, and a nut attached to the one part of the main body,
It is connected to the second part, extends in the axial direction, and is accommodated partially and coaxially in the other part of the main body part in the axial direction so as to be movable in the axial direction, and rotates the main body part A supporting rod, and
A rod piston provided integrally with the rod and accommodated in the other part of the main body so as to be rotatable and slidable in the axial direction;
A pair of elastic bodies housed in the other part of the main body and disposed on both sides of the rod piston in the axial direction;
The other portion of the main body is slidably accommodated in the axial direction, and between the rod piston and one of the pair of elastic bodies, and between the rod piston and the other of the pair of elastic bodies. And a first fluid chamber and a second fluid chamber are defined between the main body and the rod piston, respectively, and the axis line with respect to the rod. A pair of pistons movable in a direction and rotatable relative to at least one of the main body and the rod;
A fluid filled in the first and second fluid chambers,
Relative displacement between the first part and the second part generated by the vibration of the structure includes the screw shaft, the nut, the rod, the rod piston, the fluid, the piston, and the elastic body. And is transmitted to the main body portion in a state converted into rotational motion, whereby the main body portion and the rotary mass rotate, and the elastic body is pressed in the axial direction by the piston and the main body portion. Mass damper characterized by that.   A relief valve is provided on the rod piston, and further includes a relief valve that allows the first and second fluid chambers to communicate with each other in order to prevent excessive pressure of the fluid in the first and second fluid chambers. The mass damper according to claim 3. A mass damper is provided between the first part and the second part in the system including the structure to suppress vibration of the structure,
A tubular body,
A rotating mass provided integrally with the main body,
A screw shaft that is connected to the first part and extends in the axial direction of the main body part, and is partially and coaxially accommodated in one axial part of the main body part so as to be movable in the axial direction. When,
A screw that is screwed to the screw shaft via a ball, and a nut attached to the one part of the main body,
It is connected to the second part, extends in the axial direction, and is accommodated partially and coaxially in the other part of the main body part in the axial direction so as to be movable in the axial direction, and rotates the main body part A support part that supports it,
A pair of first engaging portions provided integrally with one of the main body portion and the support portion, and arranged in a state of being spaced apart from each other in the axial direction;
A second engagement portion provided integrally with the other of the main body portion and the support portion, and disposed between the pair of first engagement portions;
A pair of ones arranged between one of the pair of first engaging parts and the second engaging part, and between the other of the pair of first engaging parts and the second engaging part. An elastic body,
Relative displacement between the first part and the second part generated by the vibration of the structure is the screw shaft, the nut, the support part, the first engagement part, the elastic body, and the It is transmitted to the main body through the second engagement portion in a state of being converted into a rotational motion, whereby the main body and the rotary mass rotate with respect to the support, and the elastic body is the first Pressed in the axial direction by the first and second engaging portions,
A mass damper, further comprising a thrust bearing provided coaxially with the main body portion on a transmission path of the relative displacement including the first engagement portion, the elastic body, and the second engagement portion. A mass damper is provided between the first part and the second part in the system including the structure to suppress vibration of the structure,
A body portion integrally including a cylindrical connecting portion extending in the axial direction, and a pair of wall portions disposed in one axial position in a state of being spaced apart from each other in the axial direction;
A rotating mass provided integrally with the main body,
A screw shaft that is connected to the first part and extends in the axial direction, and is partially and coaxially accommodated in the other part of the main body part in the axial direction;
A screw that is screwed to the screw shaft via a ball, and a nut attached to the other part of the main body,
It is connected to the second part and extends in the axial direction, and is partially and coaxially accommodated in the one part of the main body part so as to be movable in the axial direction, and rotatably supports the main body part. A supporting part to
A pair of pressing portions provided integrally with the support portion, arranged in a state of being spaced apart from each other in the axial direction, and movable in the axial direction with respect to the main body portion;
An elastic body disposed between the pair of pressing portions;
It is disposed between one of the pair of pressing portions and the elastic body, and between the other of the pair of pressing portions and the elastic body, and is movable in the axial direction with respect to the main body portion and the support portion. As the support portion moves in the axial direction with respect to the main body portion, the pressing portion is pressed in the axial direction, and the pressing force of the pressing portion is changed to the elastic body. A pair of transmission parts that transmit to the wall part via,
Relative displacement between the first part and the second part generated along with the vibration of the structure is the screw shaft, the nut, the support part, the pressing part, the elastic body, the transmission part, and It is transmitted to the main body part through the wall part in a state converted into a rotational motion, whereby the main body part and the rotary mass rotate with respect to the support part,
A mass damper, further comprising a thrust bearing provided coaxially with the main body portion on the relative displacement transmission path including the pressing portion, the elastic body, the transmission portion, and the wall portion.   The mass damper according to any one of claims 3 to 6, wherein the elastic body is a disc spring unit including a plurality of disc springs stacked in the axial direction.   The mass damper according to any one of claims 1 to 7, further comprising an adjustment mass attached to at least one of the main body portion and the rotation mass and configured to adjust a rotation inertia mass of the rotation mass. .   The mass damper according to any one of claims 1 to 8, wherein the main body portion and the rotating mass are configured by members common to each other.

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