WO2008041545A1 - Dispositif d'amortissement - Google Patents

Dispositif d'amortissement Download PDF

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Publication number
WO2008041545A1
WO2008041545A1 PCT/JP2007/068541 JP2007068541W WO2008041545A1 WO 2008041545 A1 WO2008041545 A1 WO 2008041545A1 JP 2007068541 W JP2007068541 W JP 2007068541W WO 2008041545 A1 WO2008041545 A1 WO 2008041545A1
Authority
WO
WIPO (PCT)
Prior art keywords
fixed outer
working chamber
outer cylinder
viscous fluid
fixed
Prior art date
Application number
PCT/JP2007/068541
Other languages
English (en)
Japanese (ja)
Inventor
Ryoji Tomono
Yoshihito Watanabe
Original Assignee
Thk Co., Ltd.
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Thk Co., Ltd. filed Critical Thk Co., Ltd.
Priority to JP2008537470A priority Critical patent/JPWO2008041545A1/ja
Publication of WO2008041545A1 publication Critical patent/WO2008041545A1/fr

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
    • F16F9/12—Devices with one or more rotary vanes turning in the fluid any throttling effect being immaterial, i.e. damping by viscous shear effect only
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2232/00—Nature of movement
    • F16F2232/06—Translation-to-rotary conversion

Definitions

  • the present invention relates to an attenuation device that is disposed between two structures to which vibration is transmitted, and attenuates vibration energy transmitted from one structure as a vibration source to the other structure.
  • the present invention relates to an improvement of a damping device configured to convert vibration transmitted from one structure into energy of rotational motion and convert the energy of rotational motion into heat energy for consumption.
  • this damping device is provided between the first structure 100 and the second structure 101, and attenuates vibrations transmitted between them.
  • the screw rod 106 is formed with a spiral thread groove, and a screw nut 108 that is rotatably supported with respect to the fixed outer cylinder 107 is screwed into the screw groove. That is, the screw rod 106 and the screw nut 108 constitute a ball screw.
  • a cylindrical rotating inner cylinder 109 is fixed to the screw nut 108, and the outer peripheral surface of the rotating inner cylinder 109 faces the inner peripheral surface of the fixed outer cylinder 107 and forms a viscous fluid working chamber 110.
  • the screw rod 106 moves forward and backward with respect to the screw nut 108, and
  • the force and the screw nut 108 rotate with respect to the fixed outer cylinder 107, and the rotating inner cylinder 109 fixed to the screw nut 108 also rotates with respect to the fixed outer cylinder 107.
  • the gap between the outer peripheral surface of the rotating inner cylinder 109 and the inner peripheral surface of the fixed outer cylinder 107 serves as a viscous fluid working chamber 110, when the rotating inner cylinder 109 rotates, the viscous fluid in the working chamber 110 is rotated.
  • a shear frictional force according to the rotational angular velocity of the rotating inner cylinder 109 acts, and the force and the viscous fluid generate heat.
  • the vibration energy between the second structure 101 and the first structure 100 is converted into rotational energy, and the rotational energy is further converted into thermal energy.
  • the vibration energy possessed by the structure 101 of 2 is attenuated effectively.
  • the damping device for example, in a structural frame of a building structure, an example in which the damping device is arranged like a brace connecting opposing corners of the structural frame can be given.
  • an axial tensile force or compressive force acts on the damping device, and the screw rod advances and retreats with respect to the fixed outer cylinder.
  • the above-described attenuation effect is exhibited.
  • the distortion energy of the structural frame is absorbed, and the shaking of the building structure is effectively damped.
  • an example of using it together with a seismic isolation device as an earthquake countermeasure can be given.
  • the seismic isolation device is installed between the building structure and its base, and is used to insulate the building structure from the shaking of the base. Even if vibration energy due to earthquakes propagates to the building structure, The building structure can swing with its own vibration period regardless of the vibration period of the foundation. However, since the seismic isolation device insulates the shaking of the base from the shaking of the building, the shaking of the building structure will remain after the earthquake has stopped. For this reason, when the damping device described above is provided between the base and the building and building structure, the vibration energy of the building structure is absorbed by the damping device, and the vibration of the building structure can be converged at an early stage.
  • Patent Document 1 JP-A-10-184757
  • Patent Document 2 Japanese Patent Laid-Open No. 2002-5229
  • vibration energy is attenuated according to the shear frictional force acting on the viscous fluid in the working chamber. Is required to increase the area of the outer peripheral surface of the rotating inner cylinder facing the working chamber, or to reduce the gap between the fixed outer cylinder and the rotating inner cylinder, that is, the thickness of the working chamber.
  • the working chamber is extremely thin as in the latter case, it becomes difficult to assemble the rotating inner cylinder to the fixed outer cylinder, and high and / or high precision is required for processing the fixed outer cylinder and the rotating inner cylinder. The production becomes complicated.
  • the present invention has been made in view of such a problem, and the object of the present invention is to reduce attenuation capable of improving the damping performance without increasing the size of the apparatus compared to the conventional one. It is to provide an attenuation device.
  • another object of the present invention is to provide a buffer container that can provide force even when a buffer container for releasing a part of the pressure in the working chamber is provided in communication with the working chamber. It is an object of the present invention to provide a damping device that is easy to handle and can be easily attached to a structure without protruding from a fixed outer cylinder.
  • the damping device of the present invention includes a fixed outer cylinder that is fixed to the first structure and has a hollow portion, and is formed into a cylindrical shape. It is accommodated in the hollow part of the cylinder and is rotatably supported with respect to the fixed outer cylinder, and is fixed to the peripheral wall of the fixed outer cylinder.
  • a rotating inner cylinder that forms a cylindrical working chamber opposite to each other through the gap, and one end of which is coupled to the second structure and advances and retreats in the axial direction, and a helical thread groove is formed on the outer peripheral surface.
  • the fixed outer cylinder has a partition wall that closes one end of the hollow portion, while the rotating inner cylinder has a bottom plate facing the partition wall of the fixed outer cylinder, and is formed in a bottomed cylindrical shape.
  • a disk-shaped working chamber continuous from the cylindrical working chamber is formed between the partition wall and the bottom plate of the rotating inner cylinder, and the viscous fluid is sealed in the disk-shaped working chamber.
  • the rotating inner cylinder is formed in a bottomed cylindrical shape, and a cylindrical working chamber is formed between the peripheral wall of the fixed outer cylinder and the fixed inner cylinder.
  • a disk-shaped working chamber that is continuous from the cylindrical working chamber is formed between the outer cylinder and the partition wall. Therefore, the outer diameter and the axial length of the fixed outer cylinder are the same, and the area of the rotating inner cylinder that is in contact with the viscous fluid can be increased by the provision of the disk-like action chamber. Even if the device size is the same as that of the attenuation device, it is possible to improve the attenuation performance.
  • a disk-shaped working chamber continuous with the cylindrical working chamber is formed at one end of the cylindrical working chamber, so that the cylindrical working chamber is opened only at the end opposite to the disk-shaped working chamber. Therefore, it is sufficient to provide a sealing member for sealing the viscous fluid in the cylindrical working chamber and the disc-like working chamber only on one end side of the fixed outer cylinder and the rotating inner cylinder. For this reason, the number of seal members disposed can be minimized, and the concern about leakage of viscous fluid is reduced.
  • the disk-like action chamber exists at the axial end of the rotating inner cylinder, when the rotating inner cylinder rotates and a shearing force acts on the viscous fluid in the disk-like action chamber, An effect similar to that of the fluid bearing can be expected in the axial direction of the cylinder, and the axial force acting on the screw nut from the screw rod can be effectively loaded.
  • the disk-like action chamber is provided between the partition wall of the fixed outer cylinder and the bottom plate of the rotating cylinder, the disk shape is sandwiched between the fixed outer cylinder and the partition wall.
  • a buffer container in which a part of the viscous fluid can flow from the disk-shaped working chamber can be provided at a position facing the working chamber. Even if a buffer container is provided for the partition wall that closes the hollow part of the fixed outer cylinder, the force and the axial length of the fixed outer cylinder are only slightly increased. No protrusion is provided on the peripheral wall of the outer cylinder. Therefore, even when the buffer container is provided, the damping device can be easily handled and can be easily attached to the first structure and the second structure.
  • the rotating inner cylinder rotates with respect to the fixed outer cylinder, and the viscous fluid sealed in the cylindrical working chamber and the disk-shaped working chamber is thermally expanded by shear friction.
  • the viscous fluid force S flows into the S buffer container.
  • the rotating inner cylinder stops and the viscous fluid cools and contracts, the viscous fluid flows out of the buffer container into the disk-like working chamber.
  • the temperature of the viscous fluid rises due to shear frictional heat, and its fluidity is considered to increase.
  • the temperature of the viscous fluid has already dropped, and it is considered that the fluidity is lower than that at the inflow. Therefore, a pressure above a certain level is applied to the viscous fluid in the buffer container so that even if the fluidity is lowered, the viscous fluid can be pushed out from the buffer container to the disk-shaped working chamber. It is preferable to keep it.
  • a piston that slides in the buffer container is provided, and the piston is directed toward the partition wall of the fixed outer cylinder. It is conceivable to provide elastic means for biasing.
  • FIG. 1 is a half sectional view showing a first embodiment of an attenuation device to which the present invention is applied.
  • FIG. 2 is a perspective view showing a combination of a screw rod and a screw nut.
  • FIG. 3 is a cross-sectional view showing an example of a combined structure of a fixed outer cylinder and a rotor.
  • FIG. 4 is a sectional view of III Ill spring in FIG.
  • FIG. 5 is a cross-sectional view showing a conventional damping device.
  • FIG. 1 shows a first embodiment of an attenuation device to which the present invention is applied.
  • the damping device 1 attenuates the relative vibration existing between the first structure and the second structure, and converges the vibration at an early stage. It is placed between the base and used.
  • the damping device 1 includes a fixed outer cylinder 10 having a hollow portion and formed in a cylindrical shape, and is accommodated in the hollow portion of the fixed outer cylinder 10 and is rotatable with respect to the fixed outer cylinder 10
  • a rotating inner cylinder 20 supported on the rotating inner cylinder 20 a screw rod 30 having a tip inserted into the rotating inner cylinder 20, and a screw nut 40 screwed into the screw rod and fixed to the rotating inner cylinder 20.
  • the fixed outer cylinder 10 is fixed to a building as a first structure using a bolt or the like
  • the screw rod 30 is a disc-shaped mounting plate 32 provided at one end thereof. It is fixed to the base as the second structure through.
  • the fixed outer cylinder 10 has a peripheral wall 11 with a constant inner diameter and is formed in a cylindrical shape, and one end of a hollow portion surrounded by the front peripheral wall 11 is closed by a partition wall 12 as a whole. Is formed in a bottomed cylindrical shape.
  • An outer ring of a rotary bearing 13 is fixed to an open end opposite to the partition wall 12, and the rotary inner cylinder 20 is supported in the hollow portion via the rotary bearing 13.
  • the rotating inner cylinder 20 is formed in a cylindrical shape having an outer diameter smaller than the inner diameter of the peripheral wall 11 of the fixed outer cylinder 10, and is formed in the hollow portion of the fixed outer cylinder 10 by the rotating bearing 13. It is supported by.
  • the rotating inner cylinder 20 has a bottom plate 21 facing the partition wall 12 of the fixed outer cylinder 10 and is formed in a bottomed cylinder shape smaller than the fixed outer cylinder 10 as a whole.
  • the inner ring of the rotating bearing 13 is fixed to the end of the opened rotating inner cylinder 20 on the side opposite to the bottom plate 21, and the screw nut 40 is fixed to the inner ring via a bracket 22.
  • the outer diameter of the screw rod 30 into which the screw nut 40 is screwed is set to be smaller than the inner diameter of the rotating inner cylinder 20, and the tip of the screw 30 passing through the screw nut 40 is inside the hollow portion of the rotating inner cylinder 20. It is configured to be purchased.
  • the rotating inner cylinder 20 and the peripheral wall 11 of the fixed outer cylinder 10 are opposed to each other with a predetermined gap, and a cylindrical working chamber 50 filled with a viscous fluid is formed between them. Yes. Also, the above The bottom plate 21 of the rotating inner cylinder 20 and the partition wall 12 of the fixed outer cylinder 10 are also opposed to each other with a predetermined gap, and a disk-shaped working chamber 51 filled with a viscous fluid is formed therebetween.
  • the rotating inner cylinder 20 is supported by the fixed outer cylinder 10 in a so-called cantilever structure because the rotating inner cylinder 20 is supported on the peripheral wall 11 of the fixed outer cylinder 10 only by the rotary bearing 13 provided at the open end thereof.
  • the disk-shaped working chamber 51 located at one end in the axial direction of the rotating inner cylinder 20 communicates with the cylindrical working chamber 50 located around the rotating inner cylinder 20, and the viscous fluid is in a cylindrical action. It can flow freely between the chamber 50 and the disk-shaped working chamber 51.
  • a ring-shaped sealing member 25 is fitted to one end of the cylindrical working chamber 50 adjacent to the rotary bearing 13 to prevent the viscous fluid sealed in the cylindrical working chamber 50 from leaking out. is doing.
  • silicone oil having a kinematic viscosity of about 100,000 to 500,000 mm 2 / s (25 ° C.) is used as the viscous fluid enclosed in the cylindrical working chamber 50 and the disc-like working chamber 51.
  • FIG. 2 is a perspective view showing a combination of the screw rod 30 and the screw nut 40.
  • a spiral ball rolling groove 31 is formed on the outer peripheral surface of the screw rod 30, and the screw nut 40 is screwed into the script 30 via a plurality of balls 3 rolling in the ball rolling groove 31.
  • the screw nut 40 has a through-hole through which the screw rod 30 is passed and is formed in a cylindrical shape, and also circulates the ball 3 that has rolled in the ball rolling groove 31 of the screw rod 30.
  • An infinite circuit is provided. That is, these screw nut 40 and screw rod 30 constitute a ball screw.
  • a flange portion 41 is provided on the outer peripheral surface of the screw nut 40.
  • a fixing bolt 42 threaded through the flange portion 41 is fastened to the bracket 22 as shown in FIG.
  • the bracket 22 passes through the inner ring of the rotary bearing 13 and is fastened to the axial end surface of the rotary inner cylinder 20 with bolts, and protrudes from the end of the peripheral wall 11 of the fixed outer cylinder 10 in the axial direction.
  • the flange portion 41 of the screw nut 40 is fixed to the end portion of the bracket 22 protruding from the fixed outer cylinder 10. Therefore, the screw nut 40 is not accommodated in the fixed outer cylinder 10.
  • the assembly of the fixed outer cylinder 10 and the rotating inner cylinder 20 can be easily removed from the screw rod 30 by releasing the fastening of the fixing bolt 42.
  • the screw nut 40 converts the forward / backward movement along the X direction of the screw rod 30 into the rotational movement of the rotating inner cylinder 20. Therefore, the screw nut 40 has an axial direction of the screw rod 30.
  • the external force along is acting.
  • the only roller bearing 13 that supports the rotation of the rotating cylinder 20 is a cross roller bearing that can equally apply a radial load and a thrust load.
  • the thrust load acting on 20, that is, the external force acting in the axial direction of the screw rod 30 can be sufficiently loaded.
  • the fixed outer cylinder 10 and the rotating inner cylinder 20 are formed in a bottomed cylinder shape, and the partition wall 12 of the fixed outer cylinder 10 and the bottom plate 21 of the rotating inner cylinder 20 facing the partition wall 12 Since the disk-shaped working chamber 51 is provided between the two, the viscous fluid is compared with the damping device having only the cylindrical working chamber 50 facing the peripheral wall 11 of the fixed outer cylinder 10 as in the conventional damping device.
  • the area of the rotating inner cylinder 20 that is in contact with the contact area is enlarged, and a large damping force can be exerted accordingly.
  • the damping force is enhanced, the axial length of the fixed outer cylinder is substantially the same as that of the conventional damping device, and the damping force can be increased while avoiding an increase in the size of the device. From another point of view, if it is sufficient to exhibit the same level of damping force as before, the damping device should be Rimo / J, the ability to type S.
  • FIG. 4 shows a second embodiment of the attenuation device to which the present invention is applied.
  • a buffer container 60 that contains a viscous fluid is built in the fixed outer cylinder 10, and the viscosity is changed according to the internal pressure of the cylindrical working chamber 50 and the disk-shaped working chamber 51.
  • the fluid was configured to flow into the buffer container 60.
  • Other configurations are the same as those in the first embodiment, and the same reference numerals as those in FIG. 1 are given in FIG. 4 and the detailed description thereof is omitted.
  • a buffer container 60 is provided at a position facing the disc-like working chamber 51 with the partition wall 12 interposed therebetween.
  • the buffer container 60 is partitioned by a cylindrical sleeve 61 formed integrally with the peripheral wall 11 of the fixed outer cylinder 10, an end cap 62 that closes the sleeve 61, and the partition wall 12. 12 is formed with a through hole 63 leading to the disk-shaped working chamber 51! /.
  • a piston 64 that slides in the container 60 along the axial direction of the fixed outer cylinder 10, and the piston 64 and the end cap 62 are disposed.
  • a spring 65 is provided as an elastic means for urging the piston 64 toward the partition wall 12.
  • a bellows 66 force S is provided between the outer peripheral edge of the piston 64 and the end cap 62 to prevent leakage of viscous fluid between the piston 64 and the sleeve 61.
  • the piston 64 moves in the sleeve 61 in the axial direction in accordance with the amount of the viscous fluid flowing into the buffer container 60 from the through hole 63, so that the capacity of the buffer container 60 is variable.
  • the capacity of the buffer container 60 variable according to the inflow amount of the viscous fluid in this way, it is possible to prevent air from being mixed with the viscous fluid in the buffer container 60.
  • the piston 64 urges the piston 64 toward the partition wall 12 by the spring 65, the viscous fluid is generated only when the internal pressure of the viscous fluid in the cylindrical action chamber 50 and the disk-like action chamber 51 rises above a certain level. It flows into the buffer container 60 through the through-hole 63.
  • the buffer container is located at a position facing the disc-like working chamber 51 with the partition wall 12 of the fixed outer cylinder 10 interposed therebetween.
  • the axial length of the fixed outer cylinder 10 is only slightly increased even if the buffer container 60 is provided. Therefore, the fixed outer cylinder 10 is approximately equal to the outer diameter of the peripheral wall 11. It becomes possible to reduce the size. Therefore, even when the buffer container is provided, it is possible to provide a damping device that can easily be attached to the structure with a force, a handling force that prevents the buffer container from protruding from the fixed outer cylinder. it can.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Damping Devices (AREA)
  • Vibration Prevention Devices (AREA)
  • Buildings Adapted To Withstand Abnormal External Influences (AREA)

Abstract

L'invention concerne un dispositif d'amortissement présentant une meilleure performance d'amortissement sans que sa taille ne soit augmentée à un niveau supérieur à la taille des dispositifs classiques. Le dispositif d'amortissement présente un tube externe fixe (10, 107), un tube interne rotatif (20, 109) reçu de manière rotative dans le creux du tube fixe (10, 107) et formant une chambre agissant comme un tube circulaire (50) conjointement avec la paroi périphérique (11) du tube externe fixe (10, 107), une tige filetée (30, 106) présentant une rainure filetée hélicoïdale formée dans sa surface périphérique externe, un écrou fileté (40, 108) en prise avec la tige filetée (30, 106) et fixé au tube interne rotatif (20, 109), et un fluide visqueux enfermé hermétiquement dans la chambre agissant comme un tube circulaire (50). Le tube externe fixe (10, 107) présente une paroi de séparation (12) destinée à fermer une extrémité du creux, et le tube interne rotatif (20, 109) présente une plaque inférieure (21) orientée face à la paroi de séparation (12) du tube externe fixe (10, 107). Entre la paroi de séparation (12) du tube externe fixe (10, 107) et la plaque inférieure (21) du tube interne rotatif (20, 109), une chambre agissant comme un disque circulaire (51) est formée dans la continuité de la chambre agissant comme un tube circulaire (50), et le liquide visqueux est enfermé hermétiquement dans la chambre agissant comme un disque circulaire (51).
PCT/JP2007/068541 2006-09-29 2007-09-25 Dispositif d'amortissement WO2008041545A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2008537470A JPWO2008041545A1 (ja) 2006-09-29 2007-09-25 減衰装置

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006-266390 2006-09-29
JP2006266390 2006-09-29

Publications (1)

Publication Number Publication Date
WO2008041545A1 true WO2008041545A1 (fr) 2008-04-10

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Application Number Title Priority Date Filing Date
PCT/JP2007/068541 WO2008041545A1 (fr) 2006-09-29 2007-09-25 Dispositif d'amortissement

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JP (1) JPWO2008041545A1 (fr)
WO (1) WO2008041545A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011241575A (ja) * 2010-05-17 2011-12-01 Toyota Home Kk 建物
CN108138894A (zh) * 2015-10-29 2018-06-08 Thk株式会社 旋转惯性质量减震器

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6472291B2 (ja) * 2015-03-23 2019-02-20 Thk株式会社 減衰装置

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS53165193U (fr) * 1977-05-31 1978-12-25
JPS63201231U (fr) * 1987-06-16 1988-12-26
JPH05248470A (ja) * 1993-01-27 1993-09-24 Nifco Inc シリンダ形オイルダンパー
JPH10184757A (ja) * 1996-12-27 1998-07-14 Sumitomo Constr Co Ltd 減衰棒およびこの減衰棒を使用する減衰装置

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS61101824U (fr) * 1984-12-10 1986-06-28

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS53165193U (fr) * 1977-05-31 1978-12-25
JPS63201231U (fr) * 1987-06-16 1988-12-26
JPH05248470A (ja) * 1993-01-27 1993-09-24 Nifco Inc シリンダ形オイルダンパー
JPH10184757A (ja) * 1996-12-27 1998-07-14 Sumitomo Constr Co Ltd 減衰棒およびこの減衰棒を使用する減衰装置

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011241575A (ja) * 2010-05-17 2011-12-01 Toyota Home Kk 建物
CN108138894A (zh) * 2015-10-29 2018-06-08 Thk株式会社 旋转惯性质量减震器
EP3369961A4 (fr) * 2015-10-29 2018-11-14 THK Co., Ltd. Amortisseur rotatif à masses d'inertie

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