JP4772531B2 - Damping damper - Google Patents

Description

  The present invention relates to a vibration damper that converts relative linear motion into rotational motion to absorb vibration energy such as earthquakes.

Conventionally, as a damping damper, linear motion is converted into rotational motion, and vibration energy is absorbed by the synergistic effect of the viscous resistance of the liquid filled between the rotating cylinder and the fixed cylinder and the frictional resistance of the screw mechanism. What is made to dampen is known (refer to patent documents 1). For example, as shown in FIG. 5, the structure of the conventional vibration damper 35 includes a screw shaft 37 and a shaft head 37a each having a male screw 36 engraved on the outer periphery, and a female screw 38 screwed into the male screw 36. A screw nut 39, a head cover 42 that is bolted to the outer cylinder head 41 by pressing the screw nut 39 via a thrust bearing 40, and a cylindrical outer cylinder head 41 that rotatably supports the screw nut 39. 43, a head cover 42, an inner cylinder head 44 to which rotational force is transmitted to the screw nut 39 via a claw, and an outer cylinder tube 46 for fixing the outer cylinder head 43 and the outer cylinder tail 45 by welding to both ends. An inner tube 47 and an inner tube tail 48 that are rotated together with the inner tube head 44, and a tail plate 49 that is fixed to the outer tube tail 44 and covered. , In a liquid 54 to be filled into the gap between the inner cylinder tube 47 and the outer cylinder tube 46, and is generally configured.
JP 2000-274474 A

  However, in the conventional damping damper 35, in the screw mechanism for converting linear motion into rotational motion, the thrust bearing structure has an enlarged outer surface of the cylindrical portion main body of the screw nut 39 as shown in FIG. Thrust bearings 40 are arranged before and after the flange portion 39a protruding from the front side. As a result, the thrust bearing member for the screw nut 39 is sandwiched and supported by outer cylinder side members such as the outer cylinder heads 41 and 43 and the head cover 42.

  The screw nut 39 is made of a material that takes account of slippage, and its thermal expansion is larger than that of the outer cylinder heads 41 and 43 and the head cover 42 that support the thrust bearing. Therefore, when the temperature of the screw nut 39 rises due to frictional heat between the screw shaft 37 and the male screw 36 due to vibration such as an earthquake, the screw nut 39 and the flange portion 39a greatly extend in the front-rear direction. Since the member on the outer cylinder head side does not extend so much, the thrust bearing portion sandwiched between the outer cylinder side members is tightened, and the rotational resistance against the screw nut 39 may increase.

  Further, if the clearance in the longitudinal direction of the thrust bearing portion is set large in advance, it becomes difficult for the linear motion of the screw shaft 37 to be converted into rotational motion with respect to vibration having a small amplitude, and such a dead zone is caused by the damping damper 35. It may be a performance defect.

  Furthermore, the screw mechanism of the damping damper 35 and the cylindrical portion that generates a damping force with a viscous material constitute independent modules, and each has a structure having bearings in the front and rear (the same as the radial bearings 50 and 51). 52, 53), the number of components increases, and the overall length of the damping damper 35 becomes longer and its weight also increases. Therefore, the restrictions on the installation of the seismic damper 35 increase and become a construction problem. In addition, the increased number of parts is disadvantageous in terms of heat transfer.

In order to alleviate the temperature rise in the screw mechanism, it may be necessary to increase the heat capacity of the screw nut 39. For this purpose, the shape of the screw nut 39 is increased and the vibration damper 35 is increased in size. It cannot be made compact.
Furthermore, as a clue to know the magnitude of the external force applied to the building due to an earthquake, etc., if it becomes possible to check the deviation of the return to origin position of the damper and the maximum stroke, it will be necessary to spend a lot of time investigating damage to the building. Disappear. The seismic damper according to the present invention has been proposed in order to solve such a problem.

The gist for solving the above-mentioned problems of the damping damper according to the present invention is to convert a relative reciprocating motion by vibration energy into a rotational motion via a screw mechanism, and to rotate by the rotational motion. Energy is attenuated by the resistance of a viscous body filled between the inner cylinder and the outer cylinder that surrounds the outer cylinder and rotatably supports the inner cylinder, and the screw mechanism portion linearly moves by an external force. In a vibration control damper provided with a screw nut that is screwed into a screw shaft to be rotated coaxially, between the fixed outer cylinder side member and the rotating inner cylinder side member, the An angle storage means for storing a rotation angle centered on the damping damper axis of the inner cylinder side member is provided .

In addition, a relative reciprocating motion by vibration energy is converted into a rotational motion through a screw mechanism, and an outer cylinder that is rotated by the rotational motion and an outside thereof are surrounded so as to rotatably support the inner cylinder. Damping the energy by the resistance of the viscous material filled between the cylinders, and the screw mechanism part is provided with a screw nut that is screwed into a screw shaft that moves linearly by an external force and rotated as a coaxial core. In the damper, there is provided a displacement storage means for storing the maximum displacement in the direction along the axis of the damping damper and the current displacement between the fixed outer cylinder side member and the screw shaft moving linearly. .
Further, in the vibration damping damper, the screw nut is fixed to the inside of the inner cylinder head fixed to the front part of the inner cylinder via a flange part, and fixed to the flange part of the screw nut and the front part of the screw nut. The thrust bearing member for the screw nut is provided between the thrust receiving member and the thrust receiving member.

  According to the vibration damping damper of the present invention, the screw nut is forcibly rotated by the linear motion of the screw shaft, and the screw nut is thermally expanded by the frictional heat generated at that time, but the screw nut extends in the front-rear direction. Even if there is, the thrust receiving member on the front side moves forward. Therefore, since the thrust bearing member is in the rear portion of the thrust receiving member in the front-rear direction, it is not tightened by the flange of the screw nut. Thus, an increase in the rotational resistance of the screw nut is prevented. In the conventional example, since the thrust bearing member is sandwiched in the front-rear direction by the outer cylinder side member of the vibration damping damper, when the screw nut of the inner cylinder side member of the vibration damping damper is thermally expanded, the thrust bearing member However, since this is solved by the present invention, it is not tightened.

  In addition, since the thrust bearing member is not tightened in the front-rear direction, it is possible to reduce the clearance in the front-rear direction on mounting, and the screw nut rotates sensitively to a linear motion of a small stroke of the screw shaft. As a result, the dead zone is minimized and the energy attenuation characteristic is improved.

  Since the thrust receiving member is located further forward than the head portion of the outer cylinder and is exposed to the outside, the screw nut fixed with the thrust receiving member and the bolt rises in temperature due to frictional heat. The heat is transferred to the thrust receiving member and radiated to the outside. Thus, the heat capacity of the screw nut is increased, and the shape of the thrust receiving member can be increased without being restricted by the outer cylinder head, so that the heat dissipation effect is enhanced and the cooling is efficiently performed.

  By fixing the screw nut to the inner cylinder head that is rotatably supported by the outer cylinder head with the axis of each other being coaxial, the screw nut is rotatably supported by the outer cylinder head via the inner cylinder head. Therefore, the number of radial bearings for rotatably supporting the inner cylinder and the screw nut is reduced by half. That is, in the conventional example, the screw mechanism and the cylindrical portion that generates the damping force by the viscous material constitute independent modules, and each has a structure having radial bearings in the front and rear. Since only the cylindrical part is supported rotatably by the radial bearing, the number of parts of the radial bearing is halved, thereby shortening the overall length of the device, simplifying the structure of the device head, and reducing the overall weight of the device. It will be

  Furthermore, in the damping damper, the angle storage means around the damper device axis for measuring the magnitude of the external force between the fixed outer cylinder side and the rotating inner cylinder side, and the magnitude of the external force By providing displacement storage means for indicating the maximum displacement in the axial direction of the damper device for measurement and the current displacement, it is possible to easily confirm the operation history of the damper from the outside. In addition, damage to buildings and the like can be estimated in a short time, and the recovery time can be shortened.

  The vibration control damper 1 according to the present invention will be described. In addition, the same code | symbol as a prior art example is attached | subjected and demonstrated to the same thing as a prior art example. As shown in FIG. 1, the damping damper 1 converts a relative reciprocating motion by vibration energy into a rotational motion through a screw mechanism, and surrounds an inner cylinder rotated by the rotational motion and the outside thereof. Thus, energy is attenuated by the resistance of a viscous material filled between the outer cylinder and the outer cylinder that rotatably supports the inner cylinder. A male screw 36 is engraved on the outer circumference along the axis a of the damper device. There are provided rod-shaped screw shaft 37 and shaft head 37a.

  The screw shaft 37 reciprocates along the front-rear direction due to vibration such as an earthquake. A screw nut 2 having a female screw 38 screwed to the male screw 36, and a plurality of screw nuts 2 are arranged in the circumferential direction on the front end surface of the flange 2a in the cylindrical inside of the cylindrical inner cylinder head 3. The inner cylinder head 3 is fixed with a bolt 5 inserted into a bolt hole provided. The screw nut 2 and the inner cylinder head 3 are fixed coaxially along the axis a of the damping damper 1.

  The inner cylinder head 3 is fixed to a front end portion of an inner cylinder tube 47 which is an inner cylinder. An inner cylinder tail 48 is fixed to the rear portion of the inner cylinder tube 47. There is an outer cylinder tube 47 that is an outer cylinder so as to surround the inner cylinder tube 47, and an outer cylinder tail 45 and an outer cylinder head 4 are fixed to both ends of the outer cylinder tube 47 by welding. A tail plate 49 is fixed to the outer cylinder tail 45 with a bolt and closed. The structure of the rear side of the damping damper 1 is almost the same as in the conventional example.

  There is a desired gap between the outer tube 46 and the inner tube 47, and the viscous liquid 54 is filled. The inner cylinder head 3, the inner cylinder tube 47, and the inner cylinder tail 48 are axially arranged by radial bearings 50 and 51 for radial bearings provided inside the outer cylinder tail 45 and the outer cylinder head 4. It is rotatably supported coaxially with a. Therefore, the inner cylinder tube 47, the inner cylinder tail 48, the inner cylinder head 3 and the screw nut 2 are integrally rotated in the same direction.

  A thrust bearing 40 for thrust bearings is disposed in front of the bolt 5 in the flange 2a of the screw nut 2. Then, the head cover 6 having the screw nut insertion hole provided at the center is fixed to the front end face of the outer cylinder head 4 with a bolt 7, whereby the radial bearing 51 and the thrust bearing 40 are moved forward. It is pressed so as not to come out.

  A concave step is provided around the screw nut insertion hole in the front portion of the head cover 6, and a thrust bearing 8 for the screw nut 2 is provided there. Then, a thrust receiving member 9 is fixed to the front end surface of the screw nut 2 by a bolt 10.

  The thrust receiving member 9 is attached so that the thrust bearing 8 does not come out in the front-rear direction. The clearance is made as small as possible. Thus, as shown in FIG. 1, the thrust bearing member (40, 8) for the screw nut 2 is provided between the flange portion 2a of the screw nut 2 and the thrust receiving member 9 fixed to the front portion of the screw nut 2. Is provided.

  Further, the thrust receiving member 9 is located further forward than the outer cylinder head 6 in the head portion of the outer cylinder and is exposed to the outside, and is configured to promote heat dissipation.

  As described above, in the vibration damper 1 according to the present invention, the screw nut 2 is directly fixed to the inner cylinder head 3 so as to be integrated with the inner cylinder side, and one of the radial bearings 50 and 51 on the outer cylinder side. The pair is rotatably supported. Further, since the thrust bearings 40, 8 for the screw nut 2 are sandwiched by the flange 2a and the thrust receiving member 9 not on the outer cylinder side but on the inner cylinder side, the screw nut 2 is caused by frictional heat in the screw mechanism portion. The thrust bearings 40 and 8 are not tightened in the front-rear direction even if they are thermally expanded.

  A method of using the vibration damper 1 attached to a building or the like will be described. For example, when there is an earthquake, the shaft head 37a and the screw shaft 37 fixed on the building side reciprocate in the front-rear direction. Then, the screw nut 2 screwed with the screw shaft 37 rotates around the axis a. Since the clearance of the thrust bearing member for the screw nut 2 is extremely small with respect to the linear motion of the screw shaft 37, the screw nut 2 rotates in the forward / reverse direction in response to a small stroke vibration.

  At this time, when the screw shaft 37 moves rearward, the screw nut 2 and the thrust receiving member 9 are pressed rearward, so that the thrust bearing 8 receives this axial force. Conversely, when the screw shaft 37 moves forward, the screw nut 2 is pushed forward, and the thrust bearing 40 is supported by the head cover 6 by the flange 2a and receives this axial force.

  The rotation of the screw nut 2 causes the inner cylinder head 3, the inner cylinder tube 47, and the inner cylinder tail 48 to rotate in the same direction. The rotational energy is attenuated by the viscous resistance of the liquid 5 in the gap with the outer tube 46. Further, the friction between the male screw 36 of the screw shaft 37 and the female screw 38 of the screw nut 2 attenuates the seismic energy and generates frictional heat, which is transferred to the thrust receiving member 9 and transferred to the external space. The screw nut 2 is thermally radiated and thermally expanded in the front-rear direction.

  Due to the thermal expansion of the screw nut 2, the thrust receiving member 9 is also moved forward, and the clearance with the thrust bearing 8 is widened. Therefore, the rotational resistance of the screw nut 2 does not increase. Further, the length L1 of the front portion of the vibration damping damper 1 is remarkably shorter than the length L2 (see FIG. 5) of the conventional example, and the whole is reduced in size and weight.

  In another embodiment of the present invention, as shown in FIG. 2A, the magnitude of the external force is measured between the fixed outer cylinder side and the rotating inner cylinder side in the damping damper 1a. Therefore, an angle storage means A for the inner cylinder side member centering on the axis a of the damping damper is provided, and the magnitude of the external force is measured between the outer cylinder side and the screw shaft moving linearly. Displacement storage means B is provided for indicating the maximum displacement in the direction of the axis a (front-rear direction) of the seismic damper and the current displacement.

  As a specific configuration of the angle storage means A, an angle scale 11 is provided on the outer peripheral surface of the thrust receiving member 9a. Then, the entire L-shaped scale needle 12 is fastened together with a bolt 7 at a predetermined position of the head cover 6.

  As a result, as shown in FIG. 2 (B), how much the scale needle 12 has rotated from the origin can be determined from the position at which the angle scale 11 is inserted. This angle indicates the angle at which the inner cylinder tube 47, the screw nut 2 and the inner cylinder head 9a are rotated relative to the outer cylinder side, and indicates the remaining position after the end of the earthquake, I don't know the maximum value. Therefore, a mechanism to know the maximum angular displacement during an earthquake is provided.

  For this purpose, as shown in FIGS. 3 to 4, the storage shift arm 12 a is fastened together with the bolt 7 to the head cover 6 on the outer cylinder side. On the inner cylinder side, an angle scale 11 is provided on the outer peripheral surface of the thrust receiving member 9b, and a concave groove with a dovetail groove is provided in the circumferential direction, and the angle storage pieces 13, 14 that shift to the left and right are slidable. Provided.

  The angle memory pieces 13 and 14 are provided with a pressing spring 15 and a friction piece 16 on the inner side so that when the moving force disappears after the movement, the angle memory pieces 13 and 14 stay at that position. As a result, when the screw nut 2 and the thrust receiving member 9b rotate left and right in the circumferential direction at the time of an earthquake, they are pushed and moved by the storage shift arm 12, and the angle storage pieces 13 and 14 stop at the maximum movement point. And stay. Therefore, by reading the angle scale 11 at that position, the maximum rotation angle of the inner cylinder side member at the time of the earthquake can be determined.

  As shown in FIG. 2, the specific configuration of the displacement storage means B in the direction of the axis a is provided with a protrusion 37c at one location on the outer periphery of the shaft head 37b. The displacement measuring bar 17 protrudes rearward from the rear portion of the protruding portion 37c. The displacement measuring bar 17 is provided with a scale 17a and slidable amplitude recording holding pieces 17b and 17c for recording displacement in the front-rear direction.

  Further, a pointer projection 4c is provided from the outer peripheral surface of the outer cylinder head 4b toward the displacement measuring bar 17. The upper part of the pointer projection 4c is brought into contact with the side surfaces of the amplitude recording holding pieces 17b and 17c so as to move in the front-rear direction. Therefore, at the time of the earthquake, the shaft head 37c and the displacement measuring bar 17 move in the front-rear direction relative to the pointer protrusion 4c, and the amplitude record holding pieces 17b and 17c at the origin position are moved according to the amplitude. Since the amplitude record holding pieces 17b and 17c remain at the moved position, the amplitude width is read by the scale 17a. Thus, the maximum amplitude in the longitudinal direction in the earthquake is known, and after the earthquake is finished, the scale 17a is read from the position of the pointer projection 4c, and the remaining displacement is known.

  By knowing the rotation angle and amplitude, and the residual displacement, the damage investigation period after the earthquake is shortened, contributing to early recovery.

It is a longitudinal cross-sectional view of the damping damper 1 which concerns on this invention. They are the longitudinal cross-sectional view (A) of the damping damper 1a concerning the other Example of the same invention, and its one part detailed enlarged view (B). It is a longitudinal cross-sectional view of the mechanism which can know the maximum rotational angular displacement in the damping damper. It is a top view of the mechanism which can know the same maximum rotation angle displacement. It is a longitudinal cross-sectional view of the damping damper 35 concerning a prior art example. It is an expansion half sectional view of the front part of the damping damper 35 concerning the prior art example.

Explanation of symbols

1 Damping damper,
2 Screw nut, 2a flange,
3 inner cylinder head,
4 outer cylinder head, 4b outer cylinder head,
4c Pointer protrusion,
5 volts,
6 Head cover,
7 volts,
8 Thrust bearing,
9, 9a, 9b thrust receiving member,
10 volts,
11 Angle scale,
12 scale needles, 12a memory shift arm,
13 Angle memory piece,
14 angle memory piece,
15 Pressing spring,
16 friction pieces,
17 Displacement measurement bar, 17a Scale,
17b, 17c Amplitude record holding piece,
35 Damping damper,
36 male thread,
37 screw shaft, 37a shaft head,
38 female thread,
39 screw nut, 39a flange,
40 thrust bearing,
41 outer cylinder head,
42 head cover,
43 outer cylinder head,
44 inner cylinder head,
45 outer cylinder tail,
46 outer tube,
47 inner tube,
48 inner cylinder tail,
49 Tail plate,
50, 51, 52, 53 Radial bearings,
54 Liquid.

Claims (3)

A relative reciprocating motion by vibration energy is converted into a rotational motion via a screw mechanism, and an inner cylinder rotated by the rotational motion and an outer cylinder surrounding the outer cylinder and rotatably supporting the inner cylinder In the damping damper provided with a screw nut that is attenuated by the resistance of the viscous material filled between and screwed to a screw shaft that is linearly moved by an external force to be rotated coaxially with the screw mechanism.
Angle storage means for storing a rotation angle centered on a damping damper axis of the inner cylinder side member relative to the outer cylinder side member between the fixed outer cylinder side member and the rotating inner cylinder side member Established
Damping damper characterized by. A relative reciprocating motion by vibration energy is converted into a rotational motion via a screw mechanism, and an inner cylinder rotated by the rotational motion and an outer cylinder surrounding the outer cylinder and rotatably supporting the inner cylinder In a damping damper provided with a screw nut that attenuates energy by the resistance of a viscous body filled between and is screwed into a screw shaft that is linearly moved by an external force to be rotated into a coaxial core. ,
Displacement storage means for storing the maximum displacement in the direction along the axis of the damping damper and the current displacement is provided between the fixed outer cylinder side member and the screw shaft that linearly moves,
Damping damper characterized by. A screw nut is fixed inside the inner cylinder head fixed to the front part of the inner cylinder via a flange part, and between the flange part of the screw nut and a thrust receiving member fixed to the front part of the screw nut. A thrust bearing member for the screw nut is provided;
The damping damper according to any one of claims 1 and 2.

Images