JP7421191B2 - damping device - Google Patents

Description

The present invention relates to a damping device that includes an oil damper and an elastic mechanism that are connected in series.

Patent Document 1 discloses a technique for installing in a building a damping device having an oil damper and an elastic mechanism that are connected in series with each other. The damping coefficient of the oil damper and the spring constant of the elastic mechanism are designed according to the building in which the damping device is installed. However, if an error occurs during the construction of a building, the spring constant of the elastic mechanism of the oil damper may not be suitable for the building.

Japanese Patent Application Publication No. 2015-105554

Therefore, the present invention has been made in view of the above circumstances, and it is an object of the present invention to enable the spring constant of the elastic mechanism of the damping device to be adapted to the conditions at the installation site.

In order to solve the above problems, a damping device includes an oil damper and an elastic mechanism connected in series to the oil damper, and the spring constant of the elastic mechanism can be adjusted by adjusting the amount of compression.
Therefore, by adjusting the amount of compression of the elastic mechanism, the spring constant can be adjusted to suit the conditions at the installation site.

Preferably, the elastic mechanism includes a cylinder, a first end plate connected to the oil damper and provided at one end of the cylinder, a second end plate provided at the other end of the cylinder, and the second end plate. a piston rod that is inserted through the cylinder and movable in the axial direction; a flange that projects radially outward from the outer peripheral surface of the piston rod within the cylinder; and the first end plate or the an adjustment bolt that is screwed onto a second end plate and projects into the cylinder in the axial direction; a seat plate that abuts the adjustment bolt in the cylinder and is movable in the axial direction; the flange and the seat plate a first nonlinear spring sandwiched between the first and second end plates, and a second end plate that is sandwiched between the flange and an end plate on which the adjustment bolt is not screwed together; and a nonlinear spring.
Therefore, when the adjustment bolt is screwed in, the compression displacement of the first and second nonlinear springs increases, so that the spring constant of the elastic mechanism is adjusted. When the adjustment bolt is loosened, the compressive displacement of the first and second nonlinear springs is reduced, so that the spring constant of the elastic mechanism is adjusted.

According to the present invention, the spring constant of the elastic mechanism of the damping device can be adjusted to suit the conditions at the installation site.

FIG. 3 is a partial cross-sectional view showing a damping device partially cut away. 2 is an enlarged view of a portion of FIG. 1. FIG. It is a model diagram of a damping device. It is a graph showing the elastic characteristics of the elastic mechanism of the damping device. These are simulation results regarding displacement response characteristics. These are simulation results regarding acceleration response characteristics.

Embodiments of the present invention will be described below with reference to the drawings. However, since the embodiments described below are subject to various technically preferable limitations for carrying out the present invention, the scope of the present invention is not limited to the following embodiments and illustrated examples.

FIG. 1 is a partial cross-sectional view showing a part of the damping device 1, FIG. 2 is an enlarged view of a part of FIG. 1, and FIG. 3 is a dynamic model of the damping device 1. It is a drawing. This damping device 1 has both ends (that is, connecting portions 40 and 50 described below) connected to a structure such as a building, and damps vibrations of the structure by absorbing vibration energy of the structure due to earthquakes, etc. let

The damping device 1 includes an oil damper 10, an elastic mechanism 30, connecting parts 40, 50, and a connecting block 60. The oil damper 10 and the elastic mechanism 30 are connected to each other in series between the connecting portion 40 and the connecting portion 50 with a connecting block 60 interposed therebetween. Since the oil damper 10 dynamically functions as a viscoelastic body, it is modeled as a Maxwell model in which a spring 110 and a dash pod 112 are connected in series. The elastic mechanism 30 mechanically functions as a spring 130. Since the elastic mechanism 30 is connected in series to the oil damper 10, the spring constant of the damping device 1 as a whole, that is, the spring constant of the spring 110 and the spring 130 in series, is smaller than the spring constant of the spring 110 of the oil damper 10. .

The spring constant of the elastic mechanism 30 can be adjusted to suit the conditions at the site where the damping device 1 is installed. Specifically, as shown in FIG. 4, the relationship between the displacement and load of the elastic mechanism 30 is nonlinear, and as the displacement increases, the slope decreases (rigidity decreases), but the slope remains constant within a narrow range of displacement. can be considered linear. Therefore, by adjusting the initial displacement of the elastic mechanism 30, the spring constant of the elastic mechanism 30 is adjusted, and even if the elastic mechanism 30 is microscopically displaced due to an earthquake or the like, the load and displacement can be regarded as having a directly proportional relationship.

By adjusting the spring constant of the elastic mechanism 30, the spring constant of the damping device 1 as a whole, that is, the spring constant of the spring 110 and the spring 130 in series can also be adjusted.

The oil damper 10 includes a cylinder 11, a rod 12, a piston, and oil. Oil is sealed in the cylinder 11. A portion of the rod 12 is inserted into the cylinder 11, and a piston is attached to the proximal end of the rod 12, so that the rod 12 and the piston are movable in the axial direction. A piston defines a space within the cylinder 11 in the axial direction. The piston is provided with a control valve, and oil in one space partitioned by the piston passes through the control valve to the other space as the piston moves in the axial direction, and the vibration of the rod 12 is damped by the passage resistance. do. Note that a free piston may be provided in the cylinder 11 to partition a space where oil exists and a space where gas exists.

A connecting portion 40 is provided at the tip of the rod 12 of the oil damper 10, and the connecting portion 40 is rotatably connected to a structure such as a building around a pin orthogonal to the axial direction. A base end portion of the cylinder 11 is connected to the elastic mechanism 30 via a connecting block 60.

The elastic mechanism 30 includes a cylinder 31, an end plate 32, an end plate 33, a piston rod 34, a flange 35, a seat plate 36, an adjustment bolt 37, a nonlinear spring 38, and a nonlinear spring 39.

The cylinder 31 is provided in a cylindrical shape with both ends open. An end plate 32 is fixed to one end of the cylinder 31 with a bolt or the like, and an end plate 33 is fixed to the other end of the cylinder 31 with a bolt or the like. Openings at both ends of the cylinder 31 are covered by end plates 32 and 33, respectively. An opening 32a is formed in the center of the end plate 32, a connecting block 60 is fixed to the end plate 32 with bolts, etc., and the opening 32a is covered by the connecting block 60.

The piston rod 34 passes through the opening 33a of the end plate 33, and a portion of the piston rod 34 is inserted into the cylinder 31. One end of the piston rod 34 is inserted into the opening 32a of the end plate 32 within the cylinder 31, and the other end of the piston rod 34 is attached to the connecting portion 50 outside the cylinder 31. The connecting portion 50 is rotatably connected to a structure such as a building around a pin orthogonal to the axial direction.

The seat plate 36 is housed in the cylinder 31 near the end plate 33. This seat plate 36 is provided in a ring shape, and the piston rod 34 is inserted into a hole in the seat plate 36. This seat plate 36 is provided so as to be movable in the axial direction.

A flange 35 is integrally provided at the intermediate portion of the piston rod 34. The flange 35 projects radially outward from the outer peripheral surface of the piston rod 34. The flange 35 is housed within the cylinder 31 and located between the seat plate 36 and the end plate 32.

A nonlinear spring 38 is sandwiched within the cylinder 31 between the end plate 32 and the flange 35, and a nonlinear spring 39 is sandwiched within the cylinder 31 between the flange 35 and the seat plate 36. The nonlinear spring 38 is made of a disc spring laminate formed by stacking a plurality of disc springs 38a in the axial direction. The nonlinear spring 39 is also made of a disc spring laminate formed by stacking a plurality of disc springs 39a in the axial direction. The disc springs 38a, 39a are nonlinear springs, and as the amount of compression of the disc springs 38a, 39a increases, the spring constant of the disc springs 38a, 39a becomes smaller. In addition, conversely, the spring constant of the disc springs 38a, 39a may increase as the amount of compression of the disc springs 38a, 39a becomes smaller.

A plurality of female screw holes are formed in the end plate 33 at equal intervals in the circumferential direction. A plurality of adjustment bolts 37 are respectively screwed into a plurality of female threaded holes, and the tips of each adjustment bolt 37 are abutted against the seat plate 36.

In the damping device 1 described above, the spring constant of the elastic mechanism 30 can be adjusted to suit the conditions at the installation site. During adjustment, the operator rotates the adjustment bolt 37 to adjust the protrusion length of the adjustment bolt 37 from the end plate 33 into the cylinder 31, thereby adjusting the initial position of the seat plate 36 in the axial direction. Specifically, as the initial position of the seat plate 36 is moved away from the end plate 33 by the adjustment bolt 37, the amount of compression of the nonlinear springs 38 and 39 and the initial displacement of the elastic mechanism 30 increase. Thereby, the spring constant of the elastic mechanism 30 can be adjusted to a small value. On the other hand, as the initial position of the seat plate 36 is brought closer to the end plate 33 by the adjustment bolt 37, the amount of compression of the nonlinear springs 38, 39 and the initial displacement of the elastic mechanism 30 decrease. Thereby, the spring constant of the elastic mechanism 30, that is, the spring constant of the spring 130, can be largely adjusted.

Although the embodiments for carrying out the present invention have been described above, the above embodiments are intended to facilitate understanding of the present invention, and are not intended to be interpreted as limiting the present invention. Further, the present invention may be modified and improved without departing from the spirit thereof, and the present invention also includes equivalents thereof. Changes from the above embodiments will be described below. The deformation points described below may be applied in combination as much as possible.

(1) In the embodiment described above, the nonlinear spring 38 and the nonlinear spring 39 are disc spring laminates. In contrast, the nonlinear springs 38 and 39 may be, for example, round wire coil springs (eg, tapered coil springs, unequal pitch coil springs), leaf springs or square springs.

(2) In the embodiment described above, the adjustment bolt 37 is screwed into the end plate 33. Alternatively, the adjustment bolt 37 may be screwed into the end plate 32. In this case, the seat plate 36 is housed in the cylinder 31 near the end plate 32, and the tip of the adjustment bolt 37 is butted against the seat plate 36. Further, a nonlinear spring 38 is sandwiched between the seat plate 36 and the flange 35 within the cylinder 31, and a nonlinear spring 39 is sandwiched between the flange 35 and the end plate 33 within the cylinder 31.

In Examples 1 and 2, the damping device 1 is connected between an undamped main system with one degree of freedom (the main system is a model of a structure) and the foundation, and as a comparative example, the damping device 1 is connected The response characteristics of the main system were simulated for the case in which this was not the case, and the results are shown in FIGS. 5 and 6. The horizontal axis of the graph in FIG. 5 represents the vibration frequency, and the vertical axis represents the response magnification regarding displacement. The response magnification regarding displacement refers to the ratio of the relative displacement of the main system to the displacement of the foundation, and the relative displacement of the main system refers to the difference between the displacement of the main system and the absolute displacement of the foundation. The horizontal axis of the graph in FIG. 6 represents the vibration frequency, and the vertical axis represents the response magnification regarding acceleration. The response magnification regarding acceleration refers to the ratio of the absolute acceleration of the main system to the acceleration of the foundation.

When the damping device 1 is not connected as in the comparative example, the response magnification regarding displacement is determined by the following formula (1), and the response magnification regarding acceleration is determined by the following formula (2).

When the damping devices 1 are connected as in the first and second embodiments, the response magnification regarding displacement is determined by the following formula (3), and the response magnification regarding acceleration is determined by the following formula (4).

Here, in calculating the response magnification as shown in FIGS. 5 and 6, the values of each parameter were set as follows.

As is clear from FIGS. 5 and 6, when the damping device 1 is provided as in Examples 1 and 2, the response magnification is significantly reduced near the natural frequency of the main system. Furthermore, since the response characteristic of the damping device 1 of the first embodiment is different from the response characteristic of the damping device 1 of the second embodiment, if the spring constant k _a of the elastic mechanism 30 is adjusted by rotating the adjustment bolt 37, the damping device 1 It can be seen that the response characteristics can be adjusted by Therefore, by adjusting the spring constant k _a of the elastic mechanism 30 by rotating the adjustment bolt 37, the response characteristics of the damping device 1 can be optimized in accordance with the conditions at the site where the damping device 1 is installed.

1... Damping device 10... Oil damper 30... Elastic mechanism 31... Cylinder 32... End plate 33... End plate 34... Piston rod 35... Flange 36... Seat plate 37... Adjustment bolt 38... Nonlinear spring 39... Nonlinear spring

Claims (2)

oil damper and
an elastic mechanism connected in series to the oil damper,
The elastic mechanism is a damping device whose spring constant can be adjusted by adjusting the amount of compression. The elastic mechanism is
cylinder and
a first end plate connected to the oil damper and provided at one end of the cylinder;
a second end plate provided at the other end of the cylinder;
a piston rod inserted into the cylinder through the second end plate and movable in the axial direction;
a flange that protrudes radially outward from the outer peripheral surface of the piston rod within the cylinder;
an adjustment bolt that is threaded onto the first end plate or the second end plate and projects into the cylinder in the axial direction;
a seat plate that abuts the adjustment bolt in the cylinder and is movable in the axial direction;
a first nonlinear spring sandwiched between the flange and the seat plate;
2. A second nonlinear spring that is sandwiched between the flange and an end plate to which the adjustment bolt is not threadedly engaged among the first end plate and the second end plate. damping device.

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