Damper with power generation function

Abstract

To provide a damper with a power generation function, capable of suppressing the temperature rise of working fluid in association with the operation of the damper.SOLUTION: The damper with the power generation function according to this invention includes a cylinder 2 in which working oil HF is filled, a piston 3 slidably provided in the cylinder 2 for partitioning the cylinder 2 into a first fluid chamber 2e and a second fluid chamber 2f, a communication passage 4 filled with the working oil HF and communicated with the first and second fluid chambers 2e, 2f while bypassing the piston 3, a pressure motor provided in the communication passage 4 for converting the flow of the working oil HF with the slide of the piston 3 into the rotating motion of the output shaft 8, a power generation part 7 provided near the pressure motor and having an input shaft 16 extending in parallel to the output shaft 8 for generating electric power with the rotating motion of the input shaft 16, and a rotation transmission mechanism 15 for transmitting the rotation of the output shaft 8 of the pressure motor to the input shaft 16 of the power generation part 7.SELECTED DRAWING: Figure 1

Description

Technical Field

[0001] The present invention relates to a damper provided on a structure, which suppresses the vibration of the structure due to an earthquake or the like and has a power generation function of generating power by utilizing the vibration.

Background Art

[0002] Conventionally, fluid dampers such as oil dampers that obtain a damping force by the flow resistance (viscous resistance) of hydraulic oil are known. As this type of fluid damper, for example, the fluid damper disclosed in Patent Document 1 previously filed by the applicant of the present application includes a cylinder filled with a working fluid, and a piston that is movably provided in the cylinder in the axial direction and divides the inside of the cylinder into two fluid chambers. The piston is provided with a first communication passage and a second communication passage that communicate with the two fluid chambers in parallel with each other. Further, a valve (pressure regulating valve) having a first communication port and a second communication port that communicate with each of the two fluid chambers is provided in the first communication passage. The valve is configured such that the valve body moves between an open position where both the first and second communication ports are opened, a first closed position where the second communication port is opened and the first communication port is closed, and a second closed position where the first communication port is opened and the second communication port is closed in response to the pressure difference of the working fluid in the two fluid chambers.

[0003] The valve body is positioned at the second closed position by being pressed by the pressure of the fluid on the first communication port side when the pressure of the fluid on the first communication port side is higher than the pressure of the fluid on the second communication port side and the pressure difference of the fluid is equal to or greater than a first predetermined value, and is positioned at the first closed position by being pressed by the pressure of the fluid on the second communication port side when the pressure of the fluid on the second communication port side is higher than the pressure of the fluid on the first communication port side and the pressure difference of the fluid is equal to or greater than a second predetermined value.

[0004] In the fluid damper configured as described above, as an external force due to vibration is transmitted to the cylinder and the piston, and the piston moves to one side of the two fluid chambers within the cylinder, the working fluid within this one fluid chamber is pressed by the piston, and accordingly, the first communication passage is opened and closed by a valve provided in the first communication passage. As a result, the pressure of the working fluid in the two fluid chambers is adjusted, and furthermore, a damping resistance force corresponding to the pressure difference of the working fluid in the two fluid chambers, that is, the speed of the piston with respect to the cylinder, can be generated.

Prior Art Documents

Patent Documents

[0005]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0006] In a damper that obtains a damping force due to the flow resistance when the working fluid passes through an adjustment valve provided in a piston within a cylinder, like the fluid damper of Patent Document 1 described above, the vibration energy absorbed by the damper is converted into thermal energy. Therefore, the temperature of the working fluid rises as the damper operates. For this reason, for example, when the damper operates for a long time along with the response of a structure due to long-period seismic motion input, etc., when the working fluid expands due to the temperature rise, there is a risk that, for example, the capacity of an accumulator provided within a piston rod of the damper reaches its limit, or a sealing material for enclosing the working fluid within the cylinder is damaged. And due to such risks, there is a problem that there is a limit value to the amount of energy absorbed by the damper.

[0007] The present invention has been made to solve the above problems, and an object thereof is to provide a damper having a power generation function that can suppress the temperature rise of the working fluid accompanying the operation of the damper.

Means for Solving the Problems

[0008] In order to achieve the above object, a damper having a power generation function according to the invention of claim 1 includes a cylinder filled with a working fluid, a piston slidably provided in the cylinder and partitioning the inside of the cylinder into a first fluid chamber and a second fluid chamber, a communication passage filled with the working fluid, bypassing the piston and communicating with the first and second fluid chambers, a pressure motor provided in the communication passage for converting the flow of the working fluid accompanying the sliding of the piston into the rotational motion of an output shaft, a power generation unit provided in the vicinity of the pressure motor and having an input shaft extending parallel to the output shaft for generating power by the rotational motion of the input shaft, and a rotational transmission mechanism for transmitting the rotation of the output shaft of the pressure motor to the input shaft of the power generation unit.

[0009] The damper having a power generation function of the present invention is of a pressure motor type. As the piston in the cylinder slides, the working fluid in the first or second fluid chamber is pushed out and flows into the communication passage, and then flows toward the other fluid chamber. The flow of the working fluid in this communication passage is converted into a rotational motion by the pressure motor, and the rotation of the output shaft of the pressure motor is transmitted to the input shaft of the power generation unit by the rotational transmission mechanism, so that power generation is performed in the power generation unit. Further, a viscous damping effect is exhibited by the viscous resistance when the working fluid flows through the communication passage and the pressure motor and the amount of power generation. In this way, while suppressing the vibration of the structure where the damper is installed, a part of the vibration energy input to the damper can be converted into electric energy, so that the temperature rise of the working fluid can be suppressed as compared with the case of obtaining a damping effect by an adjustment valve provided on the piston.

[0010] Further, since the power generation unit has a simple configuration for generating power by the rotational motion of the input shaft that receives the rotational force from the rotational transmission mechanism, it is extremely easy to introduce and the degree of freedom of the installation location is very high. Further, as the power generation unit, an existing generator capable of generating power using the rotation of the input shaft can be directly used or used after performing simple processing on it. Furthermore, since the input shaft of the power generation unit extends parallel to the output shaft of the pressure motor, the configuration of the rotational transmission mechanism for transmitting the rotation of the output shaft of the pressure motor to the input shaft of the power generation unit can be made relatively simple. Therefore, the power generation unit and the rotational transmission mechanism can be excellent in cost performance and maintainability.

[0011] The invention according to claim 2 is a damper having the power generation function according to claim 1, wherein the power generation unit is provided such that the input shaft extends in the same direction as the output shaft of the pressure motor, and the rotational transmission mechanism has a drive pulley provided on the output shaft of the pressure motor and an endless belt stretched between the drive pulley and the input shaft of the power generation unit.

[0012] According to this configuration, the power generation unit is arranged in a position and orientation such that its input shaft extends in the same direction as the output shaft of the pressure motor. Then, by stretching an endless belt between the input shaft of the power generation unit arranged in this way and the drive pulley provided on the output shaft of the pressure motor, the rotational force of the output shaft of the pressure motor is transmitted to the input shaft of the power generation unit. In this way, since the rotational transmission mechanism can be made into a simple configuration by the arrangement of the power generation unit with respect to the pressure motor, it is possible to provide a damper having a power generation function excellent in cost performance and maintainability. Further, by changing the ratio of the outer diameter of the drive pulley to the input shaft, the rotational speed of the input shaft can be changed, so that the power generation amount by the power generation unit and the viscous damping effect accompanying the power generation amount can be easily adjusted.

[0013] The invention according to claim 3 is a damper having the power generation function according to claim 2, further comprising a rotating mass provided concentrically with the output shaft of the pressure motor and / or the input shaft of the power generation unit and exhibiting a rotational inertia mass effect by being rotationally driven by the output shaft or the input shaft.

[0014] According to this configuration, either or both of the output shaft of the pressure motor and the input shaft of the power generation unit have a rotating mass provided concentrically with the output shaft or the input shaft. By rotationally driving this rotating mass by the output shaft of the pressure motor or the input shaft of the power generation unit, the rotational inertia mass effect by the rotating mass is exhibited, and thereby the vibration suppression effect can be further enhanced.

[0015] The invention according to claim 4 is a damper having the power generation function described in claim 3, wherein a rotating mass is provided on the output shaft of the pressure motor, the communication passage and the pressure motor are provided vertically below the cylinder, and the power generation unit is provided vertically above the cylinder.

[0016] According to this configuration, while the pressure motor with the rotating mass provided on the output shaft is provided vertically below the cylinder, the power generation unit is provided vertically above the cylinder. When a rotating mass is provided on the output shaft of the pressure motor, the weight of the rotating mass acts as a downward load on the output shaft. However, in this configuration, the output shaft of the pressure motor provided vertically below the cylinder and the input shaft of the power generation unit provided vertically above the cylinder are connected by an endless belt of the rotation transmission mechanism in a state having a certain tension. With such a configuration, the output shaft of the pressure motor is supported by the input shaft of the power generation unit via the endless belt, and the load applied to the output shaft can be reduced.

[0017] Further, since the communication passage and the pressure motor are located below the fluid chamber of the cylinder, when the working fluid flows through the communication passage and the pressure motor, the pressure corresponding to the weight of the working fluid in the fluid chamber is always applied to the flowing working fluid. Thereby, the occurrence of cavitation in the working fluid flowing through the communication passage and the pressure motor can be suppressed, and damage, noise, vibration, etc. in the communication passage and the pressure motor caused by cavitation can be suppressed.

[0018] The invention according to claim 5 is a damper having the power generation function described in claim 3, wherein a rotating mass is provided on the input shaft of the power generation unit, the power generation unit is provided vertically below the cylinder, and the communication passage and the pressure motor are provided vertically above the cylinder.

[0019] According to this configuration, while the power generation unit with a rotating mass provided on the input shaft is provided vertically below the cylinder, the communication passage and the pressure motor are provided vertically above the cylinder. When a rotating mass is provided on the input shaft of the power generation unit, the weight of the rotating mass acts as a downward load on the input shaft. However, in this configuration, the input shaft of the power generation unit provided vertically below the cylinder and the output shaft of the pressure motor provided vertically above the cylinder are connected by an endless belt of the rotation transmission mechanism in a state having a certain tension. With such a configuration, the input shaft of the power generation unit is supported by the output shaft of the pressure motor via the endless belt, and the load applied to the input shaft can be reduced.

[0020] The invention according to claim 6 is a damper having the power generation function according to claim 1, wherein the pressure motor and the power generation unit are provided adjacent to each other such that the output shaft and the input shaft extend in the same direction, and the rotation transmission mechanism has a driving gear provided on the output shaft of the pressure motor and a driven gear provided on the input shaft of the power generation unit and meshing with the driving gear.

[0021] According to this configuration, the pressure motor and the power generation unit are provided adjacent to each other such that the output shaft and the input shaft extend in the same direction. Then, the driving gear provided on the output shaft of the pressure motor and the driven gear provided on the input shaft of the power generation unit mesh with each other, whereby the rotational force of the output shaft of the pressure motor is transmitted to the input shaft of the power generation unit. In this way, since the rotation transmission mechanism can be made into a simple configuration by the arrangement of the pressure motor and the power generation unit, a damper having a power generation function excellent in cost performance and maintainability can be provided. Further, by changing the gear ratio of the driving gear and the driven gear, the rotational speed of the input shaft can be changed, so that the power generation amount by the power generation unit and the viscous damping effect accompanying the power generation amount can be easily adjusted.

[0022] The invention according to claim 7 is a damper having a power generation function as described in claim 1, wherein the pressure motor and the power generation unit are provided to face each other such that the output shaft and the input shaft extend in opposite directions, and the rotation transmission mechanism has a drive gear provided on the output shaft of the pressure motor and a driven gear provided on the input shaft of the power generation unit and meshing with the drive gear.

[0023] According to this configuration, the pressure motor and the power generation unit are provided to face each other such that the output shaft and the input shaft extend in opposite directions. Then, the drive gear provided on the output shaft of the pressure motor and the driven gear provided on the input shaft of the power generation unit mesh with each other, and the rotational force of the output shaft of the pressure motor is transmitted to the input shaft of the power generation unit. In this way, since the rotation transmission mechanism can be made into a simple configuration by the arrangement of the pressure motor and the power generation unit, it is possible to provide a damper having a power generation function excellent in cost performance and maintainability. Further, by changing the gear ratio between the drive gear and the driven gear, the rotational speed of the input shaft can be changed, so that the power generation amount by the power generation unit and the viscous damping effect accompanying the power generation amount can be easily adjusted.

Brief Description of the Drawings

[0024]

Figure 1

Figure 2

Figure 3

Figure 4

Figure 5

Figure 6

Figure 7

Embodiments for Carrying Out the Invention

[0025] (Overview of Damper 1) Hereinafter, with reference to the drawings, preferred embodiments of the present invention will be described in detail. As shown in FIG. 1, a damper 1 having a power generation function according to a first embodiment of the present invention includes a cylinder 2, a piston 3 slidably provided in the cylinder 2, a communication passage 4 that bypasses the piston 3 and communicates with the inside of the cylinder 2, a gear motor 5 as a pressure motor disposed in the communication passage 4, a flywheel 9 connected to the output shaft 8 of the gear motor 5, an accumulator 21 attached to the gear motor 5, a power generation unit 7 provided in the vicinity of the gear motor 5, a rotation transmission mechanism 15 for transmitting the rotation of the output shaft 8 of the gear motor 5 to the input shaft 16 of the power generation unit 7, and the like.

[0026] The cylinder 2 integrally has a cylindrical peripheral wall 2a and first and second end walls 2b and 2c provided at both ends of the peripheral wall 2a. The internal space of the cylinder 2 is defined by these three walls 2a to 2c. A protruding portion 2d having a rod accommodation chamber 2g is integrally provided concentrically on the first end wall 2b, and a first fixture FL1 is provided at its end via a universal joint.

[0027] The piston 3 is slidably provided in the cylinder 2 in the axial direction, and divides the internal space of the cylinder 2 into a first fluid chamber 2e and a second fluid chamber 2f. The first and second fluid chambers 2e and 2f and the communication passage 4 are filled with hydraulic oil HF as a working fluid. As the hydraulic oil HF, a normal one having appropriate viscosity can be used.

[0028] The piston 3 is integrally provided with a piston rod 10 concentrically. The piston rod 10 extends from both sides of the piston 3 in the axial direction. On the side of the second end wall 2c, it penetrates the rod guide hole in a liquid-tight manner and extends outward. A second fixture FL2 is provided at the outer end of the piston rod 10 via a universal joint. Also, on the side of the first end wall 2b, the piston rod 10 penetrates the rod guide hole in a liquid-tight manner and extends into the rod housing chamber 2g of the protruding portion 2d, and a second accumulator 31 is provided at its end.

[0029] The second accumulator 31 is for storing the pressure due to the thermal expansion of the hydraulic fluid HF, etc. It has a hollow casing portion 32 formed at the end of the piston rod 10, a piston 34 slidably provided in the casing portion 32 and defining an oil chamber 33 on the piston 3 side, and a set spring 35 for biasing the piston 34 toward the oil chamber 33 side. Also, a rod communication hole 10a extending in the axial direction is formed inside the piston rod 10. The rod communication hole 10a communicates with the oil chamber 33 at one end and extends to the center of the piston 3 on the other end side.

[0030] Also, the piston 3 is formed with first and second communication holes penetrating in the axial direction and communicating with the first and second fluid chambers 2e, 2f, and a third communication hole extending in the vertical direction so as to connect the first and second communication holes and communicating with the rod communication hole 10a. Check valves 36, 36 are provided on both sides of the third communication hole in the first communication hole. Each check valve 36 is configured to allow only the flow of the hydraulic fluid HF from the third communication hole side to the first or second fluid chamber 2e, 2f side. Also, orifices 37, 37 are provided on both sides of the third communication hole in the second communication hole.

[0031] With the above configuration, when the pressure of the hydraulic fluid HF in the cylinder 2 increases with an increase in the temperature of the hydraulic fluid HF or the like, the hydraulic fluid HF gently flows from the first and second fluid chambers 2e and 2f through the second communication hole of the piston 3, the orifices 37, 37, the third communication hole, and the rod communication hole 10a into the oil chamber 33 of the second accumulator 31. Along with this, the set spring 35 is compressed via the piston 34, so that the pressure of the hydraulic fluid HF is stored in the second accumulator 31, thereby avoiding problems caused by an increase in the pressure of the hydraulic fluid HF due to a temperature rise or the like.

[0032] From this state, when the temperature of the hydraulic fluid HF decreases, the hydraulic fluid HF in the oil chamber 33 returns to the first and second fluid chambers 2e and 2f through the rod communication hole 10a, the third communication hole, the opened check valves 36, 36, and the first communication hole. As a result, the pressure stored in the second accumulator 31 is released, and it returns to the original state.

[0033] In addition, the piston 3 is formed with a first communication passage 3d and a second communication passage 3e for relief that penetrate in the axial direction. A first relief valve 11 and a second relief valve 12 are respectively provided in the first and second communication passages 3d and 3e. The first and second relief valves 11 and 12 have the same configuration as each other and are configured as normally closed valves, and have a valve body and a spring that biases the valve body in the closing direction.

[0034] The first relief valve 11 closes the first communication passage 3d until the pressure of the hydraulic fluid HF in the first fluid chamber 2e reaches a predetermined pressure, and opens the first communication passage 3d when the predetermined pressure is reached. Thereby, the pressure in the first fluid chamber 2e is released to the second fluid chamber 2f side through the first communication passage 3d and is limited to a predetermined pressure or less. Similarly, the second relief valve 12 closes the second communication passage 3e until the pressure in the second fluid chamber 2f reaches a predetermined pressure, and opens the second communication passage 3e when the predetermined pressure is reached. Thereby, the pressure in the second fluid chamber 2f is released to the first fluid chamber 2e side through the second communication passage 3e and is limited to a predetermined pressure or less.

[0035] The gear motor 5 is, for example, of the internal meshing type and is arranged at the center of the communication passage 4. The gear motor 5 has a housing 6 that communicates with the communication passage 4 via two inlets and outlets 6a, 6a, a rotatable input gear and output gear (both not shown) that are housed in the housing 6 and mesh with each other, and an output shaft 8 that is integrally provided on the output gear. Note that as the gear motor 5, a type (bidirectional pressure motor) that allows bidirectional flow of the hydraulic fluid HF between the two inlets and outlets 6a, 6a is adopted. The housing 6 is supported and fixed to the peripheral wall 2a of the cylinder 2. Further, a drain passage (not shown) for discharging the hydraulic fluid HF is provided in the housing 6. The output shaft 8 protrudes outward from the housing 6 while being liquid-tightly supported by the housing 6 via a seal (not shown). Note that as the gear motor 5, an external meshing type may be used instead of the internal meshing type.

[0036] The flywheel 9 is made of a material with a relatively large specific gravity, such as steel, and is formed, for example, in a disc shape, and is integrally provided coaxially with the output shaft 8.

[0037] The accumulator 21 is for preventing the pressure in the housing 6 of the gear motor 5 from increasing by storing the pressure of the hydraulic fluid HF in the housing 6. The accumulator 21 is of the spring type and is attached to the housing 6, and has a casing 22 that communicates with the drain passage of the housing 6 via a drain pipe 27, a piston 24 that is slidably provided in the casing 22 and defines an oil chamber 23 on the housing 6 side, and a set spring 25 that biases the piston 24 toward the oil chamber 23 side.

[0038] The drain pipe 27 communicates with the oil chamber 23 of the accumulator 21 and the housing 6 of the gear motor 5, branches off from the middle thereof, and is connected to the portion on the first fluid chamber 2e side and the portion on the second fluid chamber 2f side of the communication passage 4, respectively. Further, check valves 28, 28 for draining are provided in the drain pipe 27. The check valves 28, 28 are configured to allow only the flow of the hydraulic fluid HF from the accumulator 21 to the communication passage 4 side.

[0039] (Power generation unit 7 and rotational transmission mechanism 15) The power generation unit 7 is composed of, for example, a synchronous generator such as an alternator having a coil as an armature and a permanent magnet as a field magnet, and is arranged in the vicinity of the gear motor 5. The power generation unit 7 may have, inside, a rotor that is rotationally driven by the rotation of the input shaft 16 and a stationary stator facing the rotor (both not shown), and generates electric power by causing an induced current to flow in the coil due to the rotation of the rotor. Therefore, it does not necessarily have to be a dedicated design, and an existing generator can be used as the power generation unit 7.

[0040] The power generation unit 7 is supported and fixed at a position P1 on the peripheral wall of the protruding portion 2d of the cylinder 2 in such a direction that the input shaft 16 extends parallel to and in the same direction as the output shaft 8 of the gear motor 5. Note that the position where the power generation unit 7 is provided is not limited to this. As will be described later, it may be arranged anywhere as long as the rotational transmission mechanism 15 can transmit the rotational force of the output shaft 8 of the gear motor 5 to the input shaft 16 of the power generation unit 7. For example, as shown by the dashed line in FIG. 1, it may be configured to be arranged at another position P2 of the cylinder 2, or it may be attached and arranged not on the cylinder 2 but on the external structure of the damper 1 or the like. The electricity generated by the power generation unit 7 is stored, for example, in a power storage unit (not shown).

[0041] The rotational transmission mechanism 15 is for transmitting the rotation of the output shaft 8 of the gear motor 5 to the input shaft 16 of the power generation unit 7. In this embodiment, it is composed of a drive pulley 13 provided on the output shaft 8 of the gear motor 5 and an endless belt 14 stretched between the drive pulley 13 and the input shaft 16 of the power generation unit 7. Note that a protrusion or groove or the like for increasing the frictional force between the endless belt 14 may be provided at the portion of the input shaft 16 of the power generation unit 7 in contact with the endless belt 14. Also, a driven pulley may be provided on the input shaft 16 of the power generation unit, and the endless belt 14 may be configured to be stretched between the drive pulley 13 and the driven pulley.

[0042] (Operation of Damper 1) The damper 1 equipped with the power generation function configured as described above is attached between, for example, two relatively displaced parts (e.g., the upper beam and the lower beam) within a structure via the first and second fixtures FL1 and FL2, although not shown in the figure, and is used as a seismic isolation device. Hereinafter, the operation of the damper 1 equipped with the power generation function will be described.

[0043] First, when the structure is not vibrating, the damper 1 is in the initial state shown in FIG. 1, and the piston 3 is located at the center in the axial direction of the cylinder 2. From this initial state, when the structure vibrates during an earthquake or the like, the piston 3 moves within the cylinder 2 in a direction and stroke corresponding to the relative displacement between the two parts of the structure. Along with the movement of this piston, the hydraulic oil HF in the first or second fluid chamber 2e, 2f is pushed out by the piston 3 and flows into the communication passage 4, and after flowing through the housing 6 of the gear motor 5, it flows into the second or first fluid chamber 2f, 2e.

[0044] The pressure due to the flow of this hydraulic oil HF is converted into the rotational movement of the input gear and the output gear of the gear motor 5, and the flywheel 9 integrated with the output shaft 8 is rotationally driven, thereby exerting the rotational inertia mass effect (inertial force). In addition, a viscous damping effect (viscous force) is exerted by the viscous resistance when the hydraulic oil HF flows through the communication passage 4 and the gear motor 5 and the amount of power generation described later, so that a vibration suppression effect of the structure is exerted in combination with the rotational inertia mass effect.

[0045] Also, the rotation of the output shaft 8 of the gear motor 5 is transmitted to the input shaft 16 of the power generation unit 7 via the rotation transmission mechanism 15. Due to the rotation of the input shaft 16, the rotor in the power generation unit 7 is rotationally driven, and power generation is performed by generating an induced current in the coil.

[0046] In this way, in the damper 1 having the power generation function of the present embodiment, in addition to the rotational inertia mass effect by the flywheel 9 functioning as a rotating mass and the viscous damping effect when the hydraulic fluid HF flows through the communication passage 4 and the gear motor 5, due to the viscous damping effect acting in accordance with the power generation amount of the power generation unit 7, while suppressing the vibration of the structure where the damper 1 is installed, a part of the vibration energy input to the damper 1 can be converted into electrical energy by the power generation unit 7. Therefore, it is possible to suppress the vibration energy absorbed by the damper 1 from being thermally converted. Thereby, since the temperature rise of the hydraulic fluid HF can be suppressed, the risk that the capacity of the second accumulator 31 reaches the limit due to the thermal expansion of the hydraulic fluid HF or that a sealing material (not shown) for enclosing the hydraulic fluid HF in the cylinder 2 is damaged can be reduced. Therefore, it becomes possible to increase the viscous damping effect of the damper 1 and to enable the damper 1 to withstand vibration for a longer time. Also, in the damper 1 having the power generation function of the present embodiment, since the absorbed vibration energy can be converted into electric power and the obtained electric power can be used as regenerative energy or sold, energy can be effectively utilized to suppress long-term operation costs.

[0047] In addition, since the power generation unit 7 has a simple configuration in which power generation is performed by the rotational motion of the input shaft 16 that receives the rotational force from the rotation transmission mechanism 15, a large-sized device is not required, introduction is extremely easy, and the degree of freedom of the installation location is also very high. Further, as the power generation unit 7, a dedicatedly designed generator is not necessarily required, and an existing generator capable of generating power by the rotation of the input shaft 16 can be directly used or used after performing simple processing on it. Furthermore, since the input shaft 16 of the power generation unit 7 is arranged to extend parallel to the output shaft 8 of the gear motor 5, the configuration of the rotation transmission mechanism 15 that transmits the rotation of the gear motor 5 to the input shaft 16 of the power generation unit 7 can be made relatively simple.

[0048] Particularly in this embodiment, the power generation unit 7 is arranged at a position and in a direction such that its input shaft 16 extends in the same direction as the output shaft 8 of the gear motor 5. The rotation transmission mechanism 15 has a simple configuration including a drive pulley 13 provided on the output shaft 8 of the gear motor 5 and an endless belt 14 stretched between the drive pulley 13 and the input shaft 16 of the power generation unit 7. Therefore, the power generation unit 7 and the rotation transmission mechanism 15 of this embodiment are excellent in cost performance and maintainability.

[0049] Also, by changing the ratio of the outer diameter of the drive pulley 13 to the outer diameter of the input shaft 16, the rotational speed of the input shaft 16 can be changed. Thus, it is possible to easily adjust the power generation amount by the power generation unit 7 and the viscous damping effect associated with the power generation amount.

[0050] In this embodiment, a flywheel 9 is provided concentrically with the output shaft 8 of the gear motor 5, and the flywheel 9 is rotationally driven by the output shaft 8 to obtain a rotational inertia mass effect. In this case, by resonating the natural period of the additional vibration system composed of the support member rigidity including the rigidity of the damper 1 and the rotational inertia mass by the flywheel 9 with the natural period of the structure to be controlled, the movement amount of the piston rod 10 can be amplified, and accordingly, the power generation amount by the power generation unit 7 can be amplified. By utilizing resonance with the structure in this way, even for a relatively small amplitude (for example, 1 mm or less) of the structure caused by traffic vibration, wind sway, etc., the flywheel 9 can be rotated multiple times (for example, several times to dozens of times), resulting in a high vibration suppression effect and enabling efficient power generation.

[0051] In addition to or instead of the flywheel 9 provided on the output shaft 8 of the gear motor 5, a flywheel provided concentrically with the input shaft 16 of the power generation unit 7 and rotationally driven by the input shaft 16 may be provided. In addition, when the working oil HF flows through the communication passage 4 and the gear motor 5, in cases where a sufficient vibration suppression effect can be obtained due to the viscous damping effect acting in accordance with the power generation amount of the power generation unit 7 in addition to the viscous damping effect during the flow, when it is not necessary to obtain the rotational inertia mass effect by the flywheel 9, the flywheel 9 may be omitted.

[0052] (Second Embodiment) FIG. 2 shows a damper 100 according to the second embodiment. This damper 100 is mainly different from the damper 1 of the first embodiment described above in the arrangement of the communication passage 4, the gear motor 5, and the power generation unit 7. In the following description, the same reference numerals are given to the same components as those of the damper 1 of the first embodiment, and the description thereof is omitted, and the description will be centered on the differences from the damper 1.

[0053] As shown in FIG. 2, in the damper 100, the communication passage 4 and the gear motor 5 are provided vertically below the cylinder 2, and the power generation unit 7 is provided at a position P3 vertically above the cylinder 2. Further, a flywheel 9 is provided on the output shaft 8 of the gear motor 5. And, similar to the first embodiment, an endless belt 14 is stretched between the drive pulley 13 provided on the output shaft 8 of the gear motor 5 and the input shaft 16 of the power generation unit 7.

[0054] As described above, the flywheel 9 is made of a material having a relatively large specific gravity such as steel, and exhibits a rotational inertia mass effect by rotating coaxially with the output shaft 8 of the gear motor 5. On the other hand, the weight of the flywheel 9 always acts as a downward load on the output shaft 8 that supports the flywheel 9. In contrast, in the damper 100 of the present embodiment, the output shaft 8 of the gear motor 5 provided vertically below the cylinder 2 and the input shaft 16 of the power generation unit 7 provided at the position P3 vertically above the cylinder 2 are connected by the endless belt 14 of the rotation transmission mechanism 15 in a state having a certain tension. Thereby, the output shaft 8 of the gear motor 5 is supported by the input shaft 16 of the power generation unit 7 via the endless belt 14, and the load applied to the output shaft 8 can be reduced.

[0055] Further, in the damper 100 of the present embodiment, since the communication passage 4 and the gear motor 5 are arranged below the fluid chambers (the first and second fluid chambers 2e and 2f) of the cylinder 2, when the hydraulic fluid HF flows through the communication passage 4 and the gear motor 5, the pressure corresponding to the weight of the hydraulic fluid HF in the fluid chamber is always applied to the flowing hydraulic fluid HF. As a result, the occurrence of cavitation in the hydraulic fluid HF flowing through the communication passage 4 and the gear motor 5 can be suppressed. Therefore, it is possible to suppress damage, noise, vibration, etc. in the communication passage 4 and the gear motor 5 caused by cavitation.

[0056] Note that the position where the power generation unit 7 is provided is not limited to the position P3 directly above the gear motor 5, and it may be arranged anywhere as long as the output shaft 8 can be supported via the endless belt 14. For example, the power generation unit 7 may be provided at a position P4 near the first end wall 2b above the cylinder 2 shown in FIG. 2, or at a position P5 above the protruding portion 2d. Further, another flywheel may be provided on the input shaft 16 of the power generation unit 7, or the flywheel 9 may not be provided on the output shaft 8 of the gear motor 5. Even in a configuration where the flywheel 9 is not provided on the output shaft 8, the load applied to the output shaft 8 can be reduced by the weight of the drive pulley 13 or the like.

[0057] (Third Embodiment) FIG. 3 shows a damper 110 according to the third embodiment. This damper 110 is different from the damper 1 of the first embodiment described above in the arrangement of the power generation unit 7 and the flywheel. In the following description, the same reference numerals are given to the same components as those in the damper 1 of the first embodiment, and the description thereof is omitted, and the description will be centered on the differences from the damper 1.

[0058] As shown in FIG. 3, in the damper 110, the communication passage 4 and the gear motor 5 are provided vertically above the cylinder 2 in the same manner as in the first embodiment described above, but the power generation unit 7 is provided at the position P6 vertically below the cylinder 2. Further, instead of the flywheel 9 provided on the output shaft 8 of the gear motor 5, a flywheel 9A is provided on the input shaft 16 of the power generation unit 7. And, in the same manner as in the first embodiment, the endless belt 14 is stretched between the drive pulley 13 provided on the output shaft 8 of the gear motor 5 and the input shaft 16 of the power generation unit 7.

[0059] The flywheel 9A may have a smaller diameter than the flywheel 9. The flywheel 9A is made of a material having a relatively large specific gravity such as steel, like the flywheel 9, and exhibits a rotational inertia mass effect by rotating coaxially with the input shaft 16 of the power generation unit 7. On the other hand, the weight of the flywheel 9A always acts as a downward load on the input shaft 16 that supports it. In contrast, in the damper 110 of the present embodiment, the output shaft 8 of the gear motor 5 provided vertically above the cylinder 2 and the input shaft 16 of the power generation unit 7 provided at the position P6 vertically below the cylinder 2 are connected by the endless belt 14 of the rotation transmission mechanism 15 in a state having a certain tension. Thereby, the input shaft 16 of the power generation unit 7 is supported by the output shaft 8 of the gear motor 5 via the endless belt 14, and the load on the input shaft 16 can be reduced.

[0060] Note that the position where the power generation unit 7 is provided is not limited to the position P6 directly below the gear motor 5, and it may be arranged anywhere as long as the input shaft 16 can be supported via the endless belt 14. For example, the power generation unit 7 may be provided at the position P7 near the first end wall 2b below the cylinder 2 shown in FIG. 3 or at the position P8 below the protruding portion 2d. Further, a configuration may be adopted in which a flywheel 9 is separately provided on the output shaft 8 of the gear motor 5, or a configuration may be adopted in which the flywheel 9A is not provided on the input shaft 16 of the power generation unit 7.

[0061] (Fourth Embodiment) FIG. 4 shows a damper 120 according to the fourth embodiment. This damper 120 differs from the damper 1 of the first embodiment described above in the arrangement of the power generation unit 7, the configuration of the rotation transmission mechanism, and the presence or absence of a flywheel. In the following description, the same reference numerals are given to the same components as those of the damper 1 of the first embodiment, and the description thereof is omitted, and the description will focus on the differences from the damper 1.

[0062] As shown in FIG. 4, in the damper 120, the power generation unit 7 is provided at a position P9 adjacent to the gear motor 5 on the cylinder 2 in a direction in which the input shaft 16 extends in the same direction as the output shaft 8 of the gear motor 5. Further, a flywheel 9 and a drive pulley 13 are not provided on the output shaft 8 of the gear motor 5. Instead, a drive gear 121 is coaxially and integrally provided. Further, a driven gear 122 that meshes with the drive gear 121 is coaxially and integrally provided on the input shaft 16 of the power generation unit 7. That is, in the damper 120 of the present embodiment, the drive gear 121 and the driven gear 122 function as a rotation transmission mechanism 123, and transmit the rotational force of the output shaft 8 of the gear motor 5 to the input shaft 16 of the power generation unit 7.

[0063] In this way, by arranging the gear motor 5 and the power generation unit 7 in such a direction and position that the output shaft 8 and the input shaft 16 extend in the same direction, the rotation transmission mechanism 123 can have a simple configuration consisting of two gears. Further, in the damper 120 of the present embodiment, by changing the gear ratio between the drive gear 121 and the driven gear 122, the rotational speed of the input shaft 16 of the power generation unit 7 can be changed. Therefore, it is easy to adjust the power generation amount by the power generation unit 7 and the viscous damping effect accompanying the power generation amount.

[0064] In the damper 120 of the present embodiment, although no flywheel is provided on the output shaft 8 of the gear motor 5 or the input shaft 16 of the power generation unit 7, a rotational inertia mass effect can be obtained by the drive gear 121 that rotates integrally with the output shaft 8 of the gear motor 5 and the driven gear 122 that rotates by meshing with the drive gear 121. The obtained rotational inertia mass effect can be adjusted by changing the weights and outer diameters of the gears 121 and 122.

[0065] In addition, the driving gear 121 and the driven gear 122 of the present embodiment can be configured by, for example, ordinary spur gears, but any gear may be used as long as it can appropriately transmit power between the driving gear 121 and the driven gear 122. In addition, in the present embodiment, the extending directions of the output shaft 8 of the gear motor 5 and the input shaft 16 of the power generation unit 7 are substantially horizontal and perpendicular to the axial direction of the cylinder 2. However, the extending directions of the output shaft 8 and the input shaft 16 are not limited to this, and they can be arranged in different directions according to the types and shapes of the driving gear 121 and the driven gear 122.

[0066] (Modification of the Fourth Embodiment) FIG. 5 shows a damper 120A according to a modification of the fourth embodiment. This damper 120A is different from the damper 120 of the above-described fourth embodiment mainly in the arrangement of the gear motor 5 and the power generation unit 7, the configuration of the driving gear and the driven gear, the configuration of the drain pipe and the piston rod 10, and the presence or absence of the accumulator 21. In the following description, the same reference numerals are given to the same components as those of the damper 120 of the fourth embodiment, and the description thereof is omitted, and the description will be centered on the differences from the damper 120.

[0067] As shown in FIG. 5, in the damper 120A, the gear motor 5 is arranged on the cylinder 2 with the output shaft 8 along the axial direction of the cylinder 2, and the power generation unit 7 is arranged at the position P10 on the cylinder 2 with the input shaft 16 facing the output shaft 8 of the gear motor 5. That is, the output shaft 8 of the gear motor 5 and the input shaft 16 of the power generation unit 7 extend in opposite directions to each other. A driving gear 121A is coaxially and integrally provided on the output shaft of the gear motor 5, and a driven gear 122A meshing with the driving gear 121A is coaxially and integrally provided on the input shaft 16 of the power generation unit 7. That is, in the damper 120A of this modification, the driving gear 121A and the driven gear 122A function as a rotation transmission mechanism 123A, and transmit the rotational force of the output shaft 8 of the gear motor 5 to the input shaft 16 of the power generation unit 7.

[0068] Even if the arrangement of the gear motor 5 and the power generation unit 7 is configured such that the output shaft 8 and the input shaft 16 extend in opposite directions to each other, the rotation transmission mechanism 123A can be configured as a simple structure consisting of two gears. Also, in the damper 120A, by changing the gear ratio between the drive gear 121A and the driven gear 122A, the rotational speed of the input shaft 16 of the power generation unit 7 can be changed. Therefore, it is easy to adjust the power generation amount by the power generation unit 7 and the viscous damping effect accompanying the power generation amount.

[0069] In this modification, since small-diameter spur gears are employed as the drive gear 121A and the driven gear 122A, the resulting rotational inertia mass effect is small. However, it is also possible to use larger-diameter gears to obtain a larger rotational inertia mass effect.

[0070] Also, in the damper 120A, no accumulator is provided in the housing 6 of the gear motor 5. The drain pipe 27A communicating with the housing 6 communicates with the second rod communication hole 10b provided inside the piston rod 10, rather than the communication passage 4. In order to enable connection with the piston rod 10 that reciprocates in the axial direction during damper operation, the drain pipe 27A is composed of, for example, a flexible member. A check valve 28A for draining is provided in the drain pipe 27A. The check valve 28A is configured to allow only the flow of the hydraulic fluid HF from the housing 6 to the second rod communication hole 10b side. The second rod communication hole 10b extends along the axial direction inside the piston rod 10, communicates with the drain pipe 27A at one end, extends to the center of the piston 3 on the other end side, and communicates with the third communication hole of the piston 3.

[0071] With such a configuration, when the pressure of the hydraulic fluid HF in the housing 6 increases as the gear motor 5 operates, the hydraulic fluid HF gently flows into the oil chamber 33 of the second accumulator 31 through the drain pipe 27A, the opened check valve 28A, the second rod communication hole 10b, and the rod communication hole 10a. This prevents the pressure in the housing 6 from increasing. Thereafter, the operation of the second accumulator 31 when the temperature of the hydraulic fluid HF decreases and the pressure drops is the same as that described in the first embodiment. In this way, in the damper 120A, since the second accumulator 31 provides the functions required of the accumulator 21 in the first to fourth embodiments, the configuration of the damper can be simplified and the cost can be reduced by omitting the accumulator.

[0072] (Fifth Embodiment) FIG. 6 shows a damper 130 according to the fifth embodiment. This damper 130 is different from the damper 1 of the first embodiment described above in that a plurality of cylinders 2 are connected by cylinder communication pipes 131, 131. In the following description, the same reference numerals are given to the same components as those of the damper 1 of the first embodiment, and the description thereof is omitted, and the description will be centered on the differences from the damper 1.

[0073] As shown in FIG. 6, in the damper 130, cylinders 2 similar to the cylinders 2 described for the damper 1 of the first embodiment are further provided, and the first fluid chambers 2e of the plurality of (two in FIG. 6) cylinders 2 and the second fluid chambers 2f are connected by the cylinder communication pipes 131, 131. Inside each cylinder 2, pistons 3 and piston rods 10 similar to the pistons 3 and piston rods 10 described for the damper 1 are provided.

[0074] With such a configuration, in the damper 130, when the structure to which the damper 130 is attached vibrates, the plurality of piston rods 10 move in parallel inside each cylinder 2. The hydraulic fluid HF in each cylinder 2 pushed out thereby merges through the cylinder communication pipe 131 and flows into the housing 6 of the gear motor 5 through the communication path 4. In this way, in the damper 130, by utilizing a plurality of piston cross-sectional areas, the inflow rate of the hydraulic fluid HF into the gear motor 5 can be increased compared to the damper 1, and thus the rotational speed of the gear motor 5 can be increased. As a result, the rotational speed of the input shaft 16 of the power generation unit 7 can also be increased via the rotational transmission mechanism 15, and the power generation amount in the power generation unit 7 can be increased. Further, since the rotational speed of the output shaft 8 of the gear motor 5 increases, the rotational speed of the flywheel 9 also increases, so that the rotational inertia mass effect can also be increased.

[0075] Note that in the damper 130, the two cylinders 2 are arranged vertically, but it is not limited to this, and different arrangement relationships such as the two cylinders 2 being arranged horizontally (the depth direction in the figure) are also possible.

[0076] (Sixth Embodiment) FIG. 7 shows a damper 140 according to the sixth embodiment. This damper 140 is different from the damper 1 of the first embodiment described above in the configuration of the gear motor and the communication passage, and the presence or absence of the accumulator 21. In the following description, the same components as those of the damper 1 of the first embodiment are denoted by the same reference numerals, and the description thereof is omitted, and the description will be centered on the differences from the damper 1.

[0077] FIG. 7(a) is a longitudinal sectional view showing the operation when the piston 3 moves to the second fluid chamber 2f side in the damper 140, and FIG. 7(b) is a longitudinal sectional view showing the operation when the piston 3 moves to the first fluid chamber 2e side. As shown in these figures, in the damper 140, the communication passage 142 and the first to fourth check valves 143, 144, 145, 146 are configured such that the hydraulic fluid HF always enters from the inlet 6b of the housing 6 and exits from the outlet 6c with respect to the gear motor 141, that is, allowing the flow of the hydraulic fluid HF in only one direction.

[0078] First, referring to FIG. 7(a), the flow of the hydraulic fluid HF when the piston 3 moves to the second fluid chamber 2f side will be described. When the piston 3 moves toward the second fluid chamber 2f side and the second fluid chamber 2f side becomes high pressure while the first fluid chamber 2e side becomes low pressure, the hydraulic fluid HF pushed out by the piston 3 flows into the communication passage 142. At this time, the flow of the hydraulic fluid HF is blocked by the second check valve 144, and the flow of the hydraulic fluid HF is allowed by the first check valve 143. The hydraulic fluid HF that has passed through the first check valve 143 is blocked from flowing by the third check valve 145, then flows into the housing 6 of the gear motor 5 from the inlet 6b, and flows through the housing 6 toward the outlet 6c. The hydraulic fluid HF that has exited the housing 6 returns to the first fluid chamber 2e when the fourth check valve 146 provided on the first fluid chamber 2e side, which is the low-pressure side, opens.

[0079] Next, with reference to FIG. 7(b), the flow of the hydraulic fluid HF when the piston 3 moves toward the first fluid chamber 2e side will be described. When the piston 3 moves toward the first fluid chamber 2e side and the first fluid chamber 2e side becomes high pressure while the second fluid chamber 2f side becomes low pressure, the hydraulic fluid HF pushed out by the piston 3 flows into the communication passage 142. At this time, the flow of the hydraulic fluid HF is blocked by the fourth check valve 146, and the flow of the hydraulic fluid HF is allowed by the third check valve 145. The hydraulic fluid HF that has passed through the third check valve 145 is blocked from flowing by the first check valve 143, then flows into the housing 6 of the gear motor 5 from the inlet 6b, and flows through the housing 6 toward the outlet 6c. The hydraulic fluid HF that has exited the housing 6 returns to the second fluid chamber 2f when the second check valve 144 provided on the second fluid chamber 2f side, which is the low-pressure side, opens.

[0080] As described above, in the damper 140 of this embodiment, the communication passage 142 and the first to fourth check valves 143, 144, 145, 146 are configured such that the hydraulic fluid HF always flows from one direction to the gear motor 141. Therefore, in the damper 140 of this embodiment, as the gear motor 141, a motor (unidirectional pressure motor) of a type that allows the flow of the hydraulic fluid HF only in one direction from the inlet to the outlet or a pressure pump can be adopted. The unidirectional pressure motor and the pressure pump are inexpensive and common compared to the bidirectional pressure motor, so the configuration of the damper can be simplified and the cost can be reduced.

[0081] In addition, in each of the above-described embodiments, in order to increase the viscous damping effect by the damper 1 and increase the power generation amount by the power generation unit 7, the following countermeasures are considered to be effective. (1) Set the outer diameter of the drive pulley 13 or the first gear provided on the output shaft 8 of the gear motor 5 to be larger than the outer diameter of the input shaft 16 or the second gear of the power generation unit 7. (2) Increase the cross-sectional area of the piston 3 and use a gear motor 5 with a small displacement volume. In this case, since the rotational speed of the gear motor 5 increases as the piston rod 10 moves, it is necessary to pay attention to the allowable rotational speed of the gear motor 5. (3) Provide a flywheel on the output shaft 8 of the gear motor 5 or the input shaft 16 of the power generation unit 7. Note that the viscous damping effect also increases by increasing the flow resistance of the hydraulic fluid HF. In this case, however, the temperature of the hydraulic fluid HF also rises significantly.

[0082] Note that the present invention is not limited to the above-described embodiments and can be implemented in various modes. In the embodiment, a gear motor is used as the pressure motor, but other types of pressure motors, such as piston motors, vane motors, and screw motors, may also be used. Further, in the embodiment, it has been described that normal hydraulic oil HF is used as the working fluid of the damper, but of course, other appropriate working fluids may be used. Furthermore, regarding the drain circuit of the pressure motor, not only the case shown in the present embodiment but also cases described in, for example, JP-A-2023-091698 may be used. The detailed configurations of the dampers shown in the embodiments of the present invention are merely examples and can be appropriately changed within the scope of the gist of the present invention.

Explanation of Signs

[0083] 1 Damper of the first embodiment 2 Cylinder 2e First fluid chamber 2f Second fluid chamber 3 Piston 4 Communication passage 5 Gear motor (pressure motor) 7 Power generation unit 8 Output shaft of the gear motor (pressure motor) 9 Flywheel (rotating mass) 9A Flywheel (rotating mass) 13 Driving pulley 14 Endless belt 15 Rotation transmission mechanism 16 Input shaft of the power generation unit 100 Damper of the second embodiment 110 Damper of the third embodiment 120 Damper of the fourth embodiment 120A Damper of a modification of the fourth embodiment 121 Driving gear 121A Driving gear 122 Driven gear 122A Driven gear 123 Rotation transmission mechanism 123A Rotation transmission mechanism 130 Damper of the Fifth Embodiment 140 Damper of the Sixth Embodiment HF Working Fluid

Claims

1. A cylinder filled with a working fluid, A piston slidably provided in the cylinder and partitioning the inside of the cylinder into a first fluid chamber and a second fluid chamber, A communication passage filled with a working fluid, bypassing the piston, and communicating with the first and second fluid chambers, A pressure motor provided in the communication passage and converting the flow of the working fluid accompanying the sliding of the piston into the rotational motion of an output shaft, A power generation unit provided in the vicinity of the pressure motor, having an input shaft extending parallel to the output shaft, and generating power by the rotational motion of the input shaft, A rotation transmission mechanism for transmitting the rotation of the output shaft of the pressure motor to the input shaft of the power generation unit, A damper having a power generation function, characterized by comprising the above.

2. The power generation unit is provided such that the input shaft extends in the same direction as the output shaft of the pressure motor, The rotation transmission mechanism has a drive pulley provided on the output shaft of the pressure motor and an endless belt wound around the drive pulley and the input shaft of the power generation unit. The damper having a power generation function according to Claim 1, characterized by the above.

3. Further comprising a rotating mass provided concentrically with the output shaft of the pressure motor and / or the input shaft of the power generation unit, and exhibiting a rotational inertia mass effect by being rotationally driven by the output shaft or the input shaft. The damper having a power generation function according to Claim 2, characterized by the above.

4. The rotating mass is provided on the output shaft of the pressure motor, The communication passage and the pressure motor are provided vertically below the cylinder, The power generation unit is provided vertically above the cylinder. The damper having a power generation function according to Claim 3, characterized by the above.

5. The rotating mass is provided on the input shaft of the power generation unit, The power generation unit is provided vertically below the cylinder, and the communication passage and the pressure motor are provided vertically above the cylinder. The damper with a power generation function according to claim 3, characterized in that.

6. The pressure motor and the power generation unit are provided adjacent to each other such that the output shaft and the input shaft extend in the same direction, and the rotation transmission mechanism includes a drive gear provided on the output shaft of the pressure motor and a driven gear provided on the input shaft of the power generation unit and meshing with the drive gear. The damper with a power generation function according to claim 1, characterized in that.

7. The pressure motor and the power generation unit are provided opposite to each other such that the output shaft and the input shaft extend in opposite directions, and the rotation transmission mechanism includes a drive gear provided on the output shaft of the pressure motor and a driven gear provided on the input shaft of the power generation unit and meshing with the drive gear. The damper with a power generation function according to claim 1, characterized in that.

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