Damper using a pressure motor

Abstract

To provide a damper using a pressure motor which can prevent an excessive load from being exerted on the pressure motor by a fly wheel to enable the pressure motor to be used stably over a long time and enable a user to grasp a state of a working fluid therein from the outside easily.SOLUTION: A damper using a pressure motor includes: a cylinder 2 filled with a working fluid HF; a piston 3 which partitions the interior of the cylinder 2 into a first fluid chamber 2e and a second fluid chamber 2f; a communication passage 4 which allows the first fluid chamber 2e and the second fluid chamber 2f to communicate with each other; a pressure motor 5 which has a rotating body 16 rotatably housed in a casing 14 communicating with the communication passage 4 and converts flow of the working fluid HF in conjunction with sliding of the piston 3 into rotational motion of the rotating body 16; a fly wheel 6 disposed between the pressure motor 5 and the cylinder 2 and coaxially connected to the rotating body 16; and a fly wheel support device 7 which is provided on an outer peripheral surface of the cylinder 2 and rotatably supports the fly wheel 6.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] The present invention relates to a damper for suppressing vibration of a structure or the like, and more particularly to a damper using a pressure motor that converts the pressure of a working fluid into rotational motion. [Background technology]

[0002] A conventional damper of this type is disclosed in Patent Document 1, which has already been filed by the present applicant. This damper includes a cylinder filled with hydraulic oil, a piston slidably provided within the cylinder and dividing the interior of the cylinder into a first fluid chamber and a second fluid chamber, a communication passage that bypasses the piston and connects the first fluid chamber and the second fluid chamber within the cylinder, a gear motor serving as a pressure motor provided in the communication passage, and a flywheel connected to the gear motor.

[0003] The gear motor is an internal type, and is provided with an outer rotor with multiple teeth (internal teeth) on the inside and an inner rotor with multiple teeth (external teeth) on the outside that mesh with the internal teeth and have one fewer external tooth than the internal teeth, both of which are rotatably mounted inside a casing that communicates with a communication passage. An output shaft that protrudes outside the casing is integrally connected to the center of the inner rotor, and a flywheel is concentrically connected to the tip of the output shaft.

[0004] The damper configured as described above is attached, for example, between two parts of a structure that undergo relative displacement. When the structure vibrates during an earthquake or other event, causing the two parts to displace relative to one another, the piston of the damper moves within the cylinder. As a result, hydraulic oil in the damper flows from one of the first and second fluid chambers into the communication passage, passes through the gear motor casing, and flows toward the other of the first and second fluid chambers. The pressure caused by the flow of hydraulic oil within the casing is converted into rotational motion of the outer and inner rotors of the gear motor, causing the flywheel connected to the output shaft of the gear motor to rotate. As the flywheel rotates, its inertial mass effect is obtained, suppressing vibration of the structure. [Prior art documents] [Patent documents]

[0005] [Patent Document 1] Japanese Patent Publication No. 2020-94680 Summary of the Invention [Problem to be solved by the invention]

[0006] In the above damper, since the flywheel is relatively heavy, a relatively large load (radial load and / or thrust load) may act on the output shaft (rotating shaft) of the gear motor in the radial direction or longitudinal direction. If these loads exceed the allowable load of the gear motor, the outer rotor and inner rotor in the gear motor may seize, resulting in problems such as the gear motor not operating properly or the gear motor's lifespan being shortened.

[0007] Furthermore, when the flywheel rotates, the inertial force of the rotation generates energy, and when this energy acts as a driving force on the gear motor, the hydraulic oil upstream of the gear motor in the communication passage is sucked in by the gear motor, causing the pressure of the hydraulic oil upstream to shift to negative pressure, which can lead to cavitation. Cavitation generates air bubbles dissolved in the hydraulic oil, and if this air gets mixed into the gear motor, it can cause problems such as damage and wear to internal components. In particular, the air collides with the rotating outer rotor and inner rotor, causing loud noise and vibration. For this reason, the damper in the aforementioned Patent Document 1 has an accumulator installed in the communication passage, which stores the pressure of the hydraulic oil and uses the stored pressure to pressurize the hydraulic oil, preventing negative pressure and preventing cavitation.

[0008] However, in the above-mentioned damper, the hydraulic oil in the cylinder, the communication passage, and the accumulator cannot be seen from the outside, and therefore it is difficult to grasp the pressure state of the hydraulic oil from the outside. For example, if a crack occurs in the damper cylinder or the communication passage, causing the hydraulic oil to be filled with less than the original appropriate amount or pressure, there is a problem in that it is not easy to discover the defect.

[0009] The present invention has been made to solve the above problems, and aims to provide a damper using a pressure motor that can prevent excessive load from being applied to the pressure motor by the flywheel, thereby allowing the pressure motor to be used stably for a long period of time, and that makes it easy to grasp the state of the internal working fluid from the outside. [Means for solving the problem]

[0010] In order to achieve the above object, the invention according to claim 1 provides an engine control system comprising: a cylinder filled with a working fluid; a piston slidably disposed within the cylinder and dividing the interior of the cylinder into a first fluid chamber and a second fluid chamber; a communication passage bypassing the piston and communicating the first fluid chamber with the second fluid chamber; a pressure motor disposed in the communication passage and having a rotor rotatably housed in a casing communicated with the communication passage, the pressure motor converting the flow of the working fluid caused by the sliding of the piston into rotational motion of the rotor; a flywheel disposed between the pressure motor and the cylinder and coaxially connected to the rotor; and a flywheel support device disposed on the outer circumferential surface of the cylinder and supporting the flywheel rotatably about an axis extending in the radial direction of the cylinder. The flywheel is provided with a protruding shaft portion that protrudes from the center toward the cylinder, and the flywheel support device has a bearing that rotatably supports the protruding shaft portion and a bearing holder that holds the bearing on the outer circumferential surface of the cylinder. It is characterized by:

[0011] This damper uses a pressure motor, and when the structure on which the damper is installed vibrates, the piston in the cylinder slides, causing the working fluid to flow through the connecting passage and the casing of the pressure motor. The pressure of the working fluid caused by this flow is converted into rotational motion of the rotor of the pressure motor, which rotates and drives the flywheel coaxially connected to the rotor. This rotation of the flywheel creates a rotational inertia effect in which a reaction force corresponding to the rotational inertia mass acts on the structure, thereby suppressing vibration of the structure.

[0012] Furthermore, a flywheel support device is provided on the outer peripheral surface of the cylinder, and this flywheel support device rotatably supports the flywheel around an axis extending in the radial direction of the cylinder. In this way, the relatively heavy flywheel is rotatably supported by the flywheel support device provided on the outer peripheral surface of the relatively strong cylinder in the damper, so that it is possible to prevent excessive loads (radial loads and / or thrust loads) from the flywheel from acting on the output shaft (rotating shaft) of the pressure motor. This allows the pressure motor to be used stably for a long period of time.

[0014] Also, the aboveAccording to this configuration, the protruding shaft portion that protrudes from the center of the flywheel toward the cylinder is rotatably supported by the bearing of the flywheel support device, and this bearing is held on the outer circumferential surface of the cylinder by the bearing holder. In this way, the flywheel support device having the above-mentioned bearing and bearing holder can firmly support the rotatable flywheel in a stable state.

[0015] Claim 2 The invention relates to: Claim 1 In the damper using a pressure motor described above, the protruding shaft portion has a shaft body having a predetermined diameter, and a flange provided at the cylinder side end of the shaft body and having a diameter larger than that of the shaft body, and the bearing has a radial bearing fitted onto the flange and a pair of thrust bearings provided in a state where the flange is sandwiched from one side and the other side.

[0016] According to this configuration, the protruding shaft portion has a shaft body with a predetermined diameter, and a flange with a diameter larger than that of the shaft body is provided at the end of the shaft body facing the cylinder. The bearing supporting the protruding shaft portion includes a radial bearing and a pair of thrust bearings, with the radial bearing fitted onto the flange and the pair of thrust bearings sandwiching the flange from one side and the other side. The radial bearing supports the radial load of the protruding shaft portion, thereby significantly reducing the radial load acting on the rotor of the pressure motor as the flywheel rotates. The pair of thrust bearings also support the thrust load of the protruding shaft portion, thereby significantly reducing the thrust load acting on the rotor of the pressure motor.

[0017] Claim 3 The invention relates to: Claim 1 In the damper using the pressure motor described above, the protruding shaft portion has a predetermined diameter, and the bearing has a radial bearing fitted onto the protruding shaft portion.

[0018] With this configuration, the protruding shaft portion has a predetermined diameter, and the bearing that rotatably supports this protruding shaft portion is a radial bearing fitted onto the protruding shaft portion, making it possible to configure a flywheel support device using a bearing with such a relatively simple configuration.

[0019] Claim 4 The invention relates to: Claim 1 In the damper using the pressure motor described above, the cylinder is arranged to extend horizontally, the flywheel is arranged below the cylinder, the protruding shaft portion has a shaft body with a predetermined diameter and a flange provided at the end of the shaft body on the cylinder side and having a diameter larger than that of the shaft body, and the bearing has a thrust bearing that supports the flange from below so that it can rotate freely.

[0020] With this configuration, the cylinder is arranged to extend horizontally, and the flywheel is arranged below the cylinder. The protruding shaft portion has a flange at the end of the shaft body facing the cylinder, and this flange is supported from below by a bearing having a thrust bearing, allowing the flange to rotate freely. This allows the weight of the flywheel to be firmly supported, even when the flywheel is arranged below the cylinder, and significantly reduces the thrust load acting on the rotor of the pressure motor.

[0021] Claim 5 The invention relates to: Claims 1 to 4The damper using the pressure motor described in any one of the above items further includes an accumulator that is provided to communicate with the communication passage, stores the pressure of the working fluid in order to prevent cavitation in the working fluid, and pressurizes the working fluid with the stored pressure, and the accumulator has a casing that communicates with the communication passage, an accumulator piston that is provided slidably within the casing, a spring that urges the accumulator piston toward the communication passage, and a detection rod that is provided integrally with the accumulator piston, extends along the sliding direction of the accumulator piston, protrudes to the outside from the casing, and detects the pressure state of the working fluid.

[0022] According to this configuration, the accumulator provided in communication with the communication passage stores the pressure of the working fluid, and the stored pressure is used to pressurize the working fluid, for example, to a pressure equal to or higher than the saturated vapor pressure. This makes it possible to prevent cavitation in the working fluid that accompanies operation of the pressure motor, and to avoid problems such as noise caused by cavitation.

[0023] In the accumulator, an accumulator piston is slidably mounted within a casing communicating with the communication passage. The accumulator piston is biased toward the communication passage by a spring, and a detection rod protruding from the casing is integrally mounted on the accumulator piston. The accumulator piston slides within the casing in response to the internal pressure of the working fluid in the communication passage, and the length of protrusion of the detection rod from the casing changes accordingly. In this way, by visually checking the protruding length of the detection rod from the outside, the state of the internal pressure of the working fluid can be determined. For example, when the protruding length of the detection rod is short, the internal pressure of the working fluid is low, whereas when the protruding length of the detection rod is long, the internal pressure of the working fluid is high. In this way, the state of the internal pressure of the working fluid can be easily grasped from outside the damper.

[0024] Claim 6 The invention relates to: Claim 5In the damper using the pressure motor described in the above, a stopper is provided inside the casing, against which the accumulator piston pressed by the working fluid abuts against the biasing force of the spring in an initial state in which the working fluid has a predetermined internal pressure, thereby preventing further movement.

[0025] According to this configuration, in an initial state in which the working fluid has a predetermined internal pressure, the accumulator piston is pressed by the working fluid and abuts against the stopper against the biasing force of the spring. If the working fluid leaks from this initial state, for example, due to a crack in the damper cylinder or the connecting passage, the internal pressure of the working fluid decreases, causing the accumulator piston to move away from the stopper and toward the connecting passage due to the biasing force of the spring. Accordingly, the protruding length of the detection rod integrated with the accumulator piston from the casing changes to become shorter. Therefore, by visually checking the change in the protruding length of the detection rod, it is possible to easily detect malfunctions in the damper caused by working fluid leakage or the like.

[0026] Claim 7 The invention relates to: Claims 1 to 6 The damper using the pressure motor described in any one of the above is characterized in that it further comprises a damping performance adjustment mechanism that is provided in the communication passage and adjusts the degree of flow of the working fluid flowing through the communication passage, thereby adjusting the damping performance of the damper.

[0027] According to this configuration, the damping performance of the damper can be easily adjusted by adjusting the flow rate of the working fluid flowing through the communication passage using the damping performance adjustment mechanism provided in the communication passage.

[0028] Claim 8The invention relates to a pressure motor having a cylinder filled with a working fluid, a piston slidably provided within the cylinder and dividing the interior of the cylinder into a first fluid chamber and a second fluid chamber, a communication passage that bypasses the piston and connects the first fluid chamber and the second fluid chamber, a rotor that is disposed in the communication passage and rotatably housed in a casing that communicates with the communication passage, and that converts the flow of the working fluid caused by the sliding of the piston into rotational motion of the rotor, a flywheel coaxially connected to the rotor, and a rotor that is fixed on the outer circumferential surface of the cylinder and supports the pressure motor and drives the flywheel. directly, and a pressure motor flywheel support device that supports the motor so that it can rotate freely.

[0029] According to this configuration, as in the above-mentioned claim 1, the rotation of the flywheel generates a rotational inertia effect in which a reaction force corresponding to the rotational inertia mass acts on the structure, thereby suppressing vibration of the structure. Also, a pressure motor-flywheel support device is fixed on the outer circumferential surface of the cylinder, and this support device supports the pressure motor and the flywheel. directly, This makes it possible to stably support the pressure motor while preventing an excessive load from being applied to the pressure motor by the flywheel, and thus makes it possible to use the pressure motor stably for a long period of time.

[0030] Claim 9 The invention relates to: Claim 8 In the damper using the pressure motor described above, the pressure motor is configured to be rotatable integrally with the rotating body and further has an output shaft protruding from the casing to the outside, the flywheel has a central shaft portion provided at its center, and the pressure motor-flywheel support device has a holder having a base portion fixed on the outer peripheral surface of the cylinder and a support wall portion provided on this base portion, and a bearing provided on the support wall portion of the holder and rotatably supporting the central shaft portion of the flywheel, and the central shaft portion of the flywheel and the output shaft of the pressure motor are coaxially connected.

[0031] According to this configuration, the pressure motor / flywheel support device has a holder and a bearing, the holder is fixed to the outer peripheral surface of the cylinder via a base, and the central shaft of the flywheel is rotatably supported by the bearing provided on the support wall of the holder. The central shaft of the flywheel is coaxially connected to the output shaft of the pressure motor. This allows the flywheel to rotate stably as the output shaft of the pressure motor rotates.

[0032] Claim 10 The invention relates to: Claim 9 In the damper using the pressure motor described above, the central shaft of the flywheel and the output shaft of the pressure motor are directly connected.

[0033] With this configuration, the center shaft of the flywheel and the output shaft of the pressure motor are directly connected, so the rotational force of the pressure motor can be transmitted directly to the flywheel via the output shaft. Also, no special connector is required to connect the center shaft of the flywheel and the output shaft of the pressure motor. This makes it possible to connect the flywheel and the pressure motor without using a special connector, and the pressure motor can efficiently rotate the flywheel.

[0034] Claim 11 The invention relates to: Claim 9 In the damper using the pressure motor described above, the central shaft of the flywheel and the output shaft of the pressure motor are connected via a predetermined connecting device while being spaced apart from each other.

[0035] According to this configuration, the central shaft of the flywheel and the output shaft of the pressure motor are connected via a predetermined connector, and the central shaft and the output shaft are spaced apart from each other. This allows the distance between the pressure motor and the flywheel to be adjusted according to, for example, the outer diameter and size of the cylinder, the length of the central shaft and the output shaft, etc., and also ensures smooth rotation of the flywheel by the pressure motor. [Brief explanation of the drawings]

[0036] [Figure 1] 1A and 1B are cross-sectional views showing a damper according to a first embodiment of the present invention in a partially cut-away state, in which (a) is a horizontal cross-sectional view of a gear motor and a flywheel in the damper of (b), and (b) is a vertical cross-sectional view of the entire damper. [Figure 2] 1(b) is an enlarged view of a flywheel support device and its surroundings in the damper shown in FIG. [Figure 3] FIG. 10 is a diagram showing a modified example of the flywheel support device. [Figure 4] FIG. 2 is an enlarged view of an accumulator in the damper shown in FIG. [Figure 5] 1A and 1B are diagrams for explaining the state when the internal pressure of the hydraulic oil acts on the accumulator, where (a) shows the initial state, (b) shows a state in which the hydraulic oil is at a higher pressure than the initial state, and (c) shows a state in which the hydraulic oil is at a lower pressure than the initial state. [Figure 6] 10 is a diagram for explaining the operation of the damper, showing the flow direction of hydraulic oil and the rotation direction of the gear motor when the piston moves leftward. FIG. [Figure 7] 7 is a view similar to FIG. 6 showing the direction of hydraulic oil flow and the direction of gear motor rotation when the piston moves to the right. [Figure 8] 10A and 10B are cross-sectional views showing a damper according to a second embodiment of the present invention in a partially cut-away state, where (a) and (b) are enlarged views of the left and right damping performance adjustment mechanisms of the damper in (c), and (c) is a longitudinal cross-sectional view of the entire damper. [Figure 9] 10 is a diagram for explaining the operation of the damper, showing the flow direction of hydraulic oil when the piston moves leftward. FIG. [Figure 10] FIG. 10 is a view similar to FIG. 9, showing the direction of hydraulic oil flow as the piston moves to the right. [Figure 11]10A and 10B are cross-sectional views showing a damper according to a third embodiment of the present invention in a partially cut-away state, in which (a) is a longitudinal cross-sectional view of the entire damper, and (b) is an enlarged view of the flywheel support device and its surroundings in the damper of (a). [Figure 12] FIG. 10 is a partially cutaway longitudinal sectional view of the entire damper according to a fourth embodiment of the present invention. [Figure 13] 1A, 1B, and 1C are enlarged views of a gear motor and a flywheel installed on a cylinder, where FIG. 1A is a plan view, FIG. 1B is a front view, and FIG. 1C is a side view. [Figure 14] 10A and 10B are enlarged views showing a modified example of the connecting structure between a gear motor and a flywheel installed on a cylinder, where (a) is a plan view, (b) is a front view, and (c) is a side view with the side wall of the holder omitted. [Figure 15] 8(a) and 8(b), respectively, and are diagrams showing modified examples of the left and right damping performance adjustment mechanisms. DETAILED DESCRIPTION OF THE INVENTION

[0037] Preferred embodiments of the present invention will be described in detail below with reference to the drawings. Fig. 1(b) shows a damper according to a first embodiment of the present invention. As shown in the figure, this damper 1 includes a horizontally extending cylinder 2, a piston 3 slidably provided within 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 (pressure motor) provided in the communication passage 4, a flywheel 6 disposed between the gear motor 5 and the cylinder 2 and connected to an output shaft 17 of the gear motor 5, a flywheel support device 7 provided in the cylinder 2 and rotatably supporting the flywheel 6, and a pair of accumulators 8, 8 provided at predetermined positions on both sides of the gear motor 5 in the communication passage 4.

[0038] The cylinder 2 has a cylindrical peripheral wall 2a and first and second end walls 2b, 2c integrally provided at both ends of the peripheral wall 2a, and these three walls 2a to 2c define the internal space of the cylinder 2. A concentric protrusion 2d is formed integrally with the first end wall 2b, and a first mounting fixture FL1 is attached to the end of the protrusion 2d via a universal joint.

[0039] The piston 3 is provided in the cylinder 2 so as to be slidable in its axial direction, and the internal space of the cylinder 2 is divided into a first fluid chamber 2e and a second fluid chamber 2f by the piston 3. These first and second fluid chambers 2e, 2f and the communication passage 4 are filled with hydraulic oil HF (working fluid) having an appropriate viscosity.

[0040] A piston rod 9 is provided concentrically and integrally with the piston 3. The piston rod 9 extends from the piston 3 toward the second end wall 2c (to the right in FIG. 1), and further extends outward while passing through a rod guide hole 2g in the second end wall 2c in a liquid-tight manner. A second mounting fixture FL2 is attached to the outer end (to the right in FIG. 1) of the piston rod 9 via a universal joint.

[0041] Furthermore, a first communication hole 3a and a second communication hole 3b that penetrate in the axial direction are formed in the piston 3. A first relief valve 11 and a second relief valve 12 are provided in the first and second communication holes 3a, 3b, respectively. The first and second relief valves 11, 12 have the same configuration, are configured as normally closed valves, and include a valve body and a spring that biases the valve body in a valve closing direction.

[0042] The first relief valve 11 closes the first communication hole 3a until the pressure of the hydraulic oil HF in the first fluid chamber 2e reaches a predetermined first predetermined pressure, and then opens the first communication hole 3a when the first predetermined pressure is reached. This allows the pressure in the first fluid chamber 2e to escape to the second fluid chamber 2f via the first communication hole 3a, limiting the pressure to below the first predetermined pressure. Similarly, the second relief valve 12 closes the second communication hole 3b until the pressure in the second fluid chamber 2f reaches the first predetermined pressure, and then opens the second communication hole 3b when the first predetermined pressure is reached. This allows the pressure in the second fluid chamber 2f to escape to the first fluid chamber 2e via the second communication hole 3b, limiting the pressure to below the first predetermined pressure.

[0043] A pair of communication ports 2h, 2h are formed in the upper portions of both ends of the peripheral wall 2a of the cylinder 2, and a communication passage 4 is connected to both communication ports 2h, 2h.

[0044] The communication passage 4 extends substantially parallel to the length of the cylinder 2 and is composed of a main passage portion 4a in which a gear motor 5 is provided, and a pair of cylinder connection passage portions 4b, 4b that extend substantially at right angles from both ends of the main passage portion 4a and are connected to the communication ports 2h, 2h of the cylinder 2. With this configuration, the communication passage 4 communicates between the first fluid chamber 2e and the second fluid chamber 2f in the cylinder 2 via both communication ports 2h, 2h.

[0045] The gear motor 5 is an internal gear motor and is disposed in the main passage portion 4a of the communication passage 4. As shown in FIG. 1(a), the gear motor 5 has a casing 14 that communicates with the communication passage 4 via two inlets and outlets 14a, 14a, an outer rotor 15 that is rotatably housed in the casing 14 and has a plurality of internal teeth on the inside, an inner rotor 16 (rotating body) that meshes with the outer rotor 15 and has a plurality of external teeth that have one less tooth than the internal teeth, and an output shaft 17 that is integrally provided at the center of the inner rotor 16. Although not shown, an external gear motor can also be used as the gear motor 5.

[0046] The flywheel 6 is made of a material with a relatively high specific gravity (for example, steel) and is formed in the shape of a disk with a predetermined diameter and thickness. A connecting hole 6a with a predetermined diameter is formed in the center of the flywheel 6, and the output shaft 17 of the gear motor 5 is inserted into this connecting hole 6a from above and is integrally connected to the flywheel 6 via a rotational torque transmission key 18. The flywheel 6 is rotatably supported from below by a flywheel support device 7.

[0047] 2 is an enlarged view of the flywheel support device 7 and its surroundings. As shown in the figure, the flywheel support device 7 has a plurality of bearings 21 (three in this embodiment) that rotatably support a protruding shaft portion 20 that protrudes from the center of the underside of the flywheel 6, and a bearing holder 22 that holds these bearings 21 on the peripheral wall 2 a of the cylinder 2.

[0048] The protruding shaft portion 20 has a shaft body 20a that extends a predetermined length in the vertical direction and has a predetermined diameter, and an upper flange 20b and a lower flange 20c that are provided at the upper and lower ends of the shaft body 20a, respectively, and have predetermined diameters larger than that of the shaft body 20a. The upper end of the shaft body 20a is inserted from below into the connecting hole 6a of the flywheel 6, and the protruding shaft portion 20 is fixed with multiple bolts 24 (only two are shown in FIG. 2 ) with the upper flange 20b abutting the underside of the flywheel 6. In this way, the protruding shaft portion 20 is integrally connected to the underside of the flywheel 6. The lower flange 20c of the protruding shaft portion 20 is accommodated in a bearing holder 22 formed in a recess in the peripheral wall 2a of the cylinder 2, with its periphery supported by a bearing 21.

[0049] The bearing 21 includes a radial bearing 21A fitted onto the lower flange 20c of the protruding shaft portion 20, and a pair of thrust bearings 21B, 21B sandwiching the lower flange 20c from the upper and lower sides thereof. These bearings 21A, 21B, 21B are housed in the bearing holder 22 together with the lower flange 20c of the protruding shaft portion 20.

[0050] A cover plate 25 that covers the open upper surface of the upper end of bearing holder 22 is fixed with multiple bolts 26 (only two are shown in FIG. 2). This cover plate 25 prevents bearings 21A, 21B, 21B housed in bearing holder 22 from moving outward, and as a result, protruding shaft 20 connected to flywheel 6 is firmly and rotatably supported in a stable state.

[0051] In the above-described flywheel support device 7, the bearings 21A, 21B, and 21B are accommodated in the bearing holding portion 22 formed in a recessed shape in the peripheral wall 2a of the cylinder 2. However, it is also possible to hold the bearings in the peripheral wall of an existing cylindrical cylinder, for example.

[0052] FIG. 3 shows a modified example of the flywheel support device 7 described above. As shown in the figure, in this flywheel 6A, a protruding shaft portion 20A having a predetermined diameter and projecting downward from the center of the underside is integral with the flywheel 6A. A radial bearing 21C is fitted onto the protruding shaft portion 20A, and a bearing holder 27 that holds the radial bearing 21C is fixed to the peripheral wall 2a of the cylinder 2A with multiple bolts 28 (only two are shown in FIG. 3). With the flywheel support device 7A configured in this way, it is relatively easy to install the bearing 21C for rotatably supporting the flywheel 6A on the peripheral wall 2a of an existing cylinder 2A.

[0053] 1, a pair of accumulators 8, 8 are provided at both ends of the main passage portion 4a of the communication passage 4. The accumulator 8 stores the pressure of the hydraulic oil HF and pressurizes the hydraulic oil HF with the stored pressure in order to prevent cavitation of the hydraulic oil HF in the gear motor 5 or the like.

[0054] 4 shows an enlarged view of the accumulator 8. As shown in the figure, the accumulator 8 includes a casing 31 communicating with the communication passage 4, an accumulator piston 32 (hereinafter referred to as the "AC piston 32") housed in the casing 31 and slidable up and down, a detection rod 33 integral with the AC piston 32 and extending upward, protruding outward from a through-hole 31a of the casing 31, and used to detect the pressure state of the hydraulic oil HF, and a set spring 34 provided in the casing 31 and biasing the AC piston 32 toward the communication passage 4 (the lower side in FIG. 4). A stopper 35 is provided at a predetermined position within the casing 31, and when the AC piston 32 abuts against the stopper 35 from below, the AC piston 32 is prevented from moving further upward.

[0055] As shown in Figure 1(b), the casing 14 of the gear motor 5 is provided with a drain 14b for the hydraulic oil HF, and this drain 14b is connected to a drain accumulator 37. This drain accumulator 37 is configured in almost the same way as the accumulator 8 connected to the communication passage 4, except that it does not have the detection rod 33 or stopper 35.

[0056] 1(b), the piston 3 and the piston rod 9 are provided with a piston accumulator 41. The piston accumulator 41 includes a flow path 42 that penetrates the piston 3 and extends into the piston rod 9, a hydraulic oil reservoir 43 that is connected to the flow path 42 and has a predetermined capacity within a predetermined end (the left end in FIG. 1(b)) of the piston rod 9, a piston 44 that is slidably provided in the hydraulic oil reservoir 43, and a spring 45 that biases the piston 44 toward the flow path 42. With the piston accumulator 41 configured in this manner, when the hydraulic oil HF thermally expands, the hydraulic oil HF flows into the hydraulic oil reservoir 43 via the flow path 42, while when the hydraulic oil HF thermally contracts, the hydraulic oil HF in the hydraulic oil reservoir 43 is supplied to the first and second fluid chambers 2e, 2f of the cylinder 2 via the flow path 42. In this way, the piston accumulator 41 absorbs the thermal expansion and contraction of the hydraulic oil HF, thereby maintaining the internal pressure of the hydraulic oil HF within a predetermined range and effectively preventing the internal pressure from becoming negative.

[0057] The damper 1 configured as above is attached, for example, between two parts of a structure that undergo relative displacement (for example, an upper beam and a lower beam) via a first attachment fixture LF1 and a second attachment fixture LF2. The operation of the damper 1 will be described below.

[0058] 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 of the cylinder 2 in the axial direction. In this case, a certain internal pressure acts on the hydraulic oil HF. As a result, as shown in Figs. 1 and 5(a), in both the left and right accumulators 8, 8 connected to the communicating passage 4, the AC piston 32 is pressed by the internal pressure of the hydraulic oil HF against the biasing force of the set spring 34, and comes into contact with the stopper 35 from below, preventing further upward movement. Therefore, in this case, in each accumulator 8, the detection rod 33 is maintained in a state in which it protrudes a predetermined length from the top surface of the casing 31.

[0059] From this initial state, when the structure vibrates during an earthquake or other event, the piston 3 moves within the cylinder 2 in accordance with the relative displacement between the two parts of the structure. Figure 6 shows the state when the piston 3 moves toward the first fluid chamber 2e on the left. In this case, the hydraulic oil HF in the first fluid chamber 2e is pushed out by the piston 3 and flows into the communicating passage 4 through the left communicating port 2h, and then into the casing 14 of the gear motor 5.

[0060] As shown in Figure 6(a), in the gear motor 5, the hydraulic oil HF flows in from the left inlet / outlet 14a of the casing 14, and due to the pressure caused by the flow, the hydraulic oil HF flows out from the right inlet / outlet 14a while rotating the outer rotor 15 and the inner rotor 16 in the casing 14 in the clockwise direction in Figure 6(a), and then flows into the second fluid chamber 2f in the cylinder 2 via the connecting passage 4.

[0061] Figure 7 shows the state when the piston 3 in the cylinder 2 moves toward the second fluid chamber 2f on the right side, opposite to Figure 6. In this case, the hydraulic oil HF in the second fluid chamber 2f is pushed out by the piston 3, flows into the communication passage 4 through the right communication port 2h, and further flows through the casing 14 of the gear motor 5 and the communication passage 4 into the first fluid chamber 2e in the cylinder 2. In this case, as shown in Figure 7(a), in the gear motor 5, the hydraulic oil HF flowing in from the right port 14a of the casing 14 and flowing out from the left port 14a causes the outer rotor 15 and inner rotor 16 in the casing 14 to rotate counterclockwise in Figure 7(a).

[0062] As described above, when the inner rotor 16 of the gear motor 5 rotates clockwise or counterclockwise, the output shaft 17 integral with it rotates, and the flywheel 6 integrally connected to this output shaft 17 via the rotational torque transmission key 18 also rotates. In this way, the rotation of the flywheel 6 produces a rotational inertia mass effect (inertia force) in the damper 1. In addition, a viscous damping effect (viscous force) is produced in the damper 1 due to the viscous resistance of the hydraulic oil HF when it flows through the communicating passage 4, etc. The reaction forces due to these rotational inertia mass effect and viscous damping effect act on the structure, thereby suppressing vibration of the structure.

[0063] Furthermore, when the gear motor 5 operates as described above, the pressure of the hydraulic oil HF in the communicating passage 4 increases compared to the initial state. In this case, in the left and right accumulators 8, 8 connected to the communicating passage 4, as the internal pressure of the hydraulic oil HF increases, the AC piston 32 is pressed against the biasing force of the set spring 34. However, as shown in FIG. 5(b), the AC piston 32 abuts against the stopper 35, preventing the AC piston 32 from moving further upward. In other words, the internal pressure of the hydraulic oil HF is maintained at an increased state by the accumulators 8, 8. In addition, in this case, the position of the AC piston 32 of each accumulator 8 is the same as in the initial state, and therefore the detection rod 33 of each accumulator 8 is also maintained in a state protruding a predetermined length from the top surface of the casing 31, as in the initial state.

[0064] Furthermore, when the flywheel 6 rotates, its rotational force may act as a driving force on the gear motor 5, in which case the internal pressure of the hydraulic oil HF decreases on the side of the communication passage 4 (hereinafter referred to as the "suction side communication passage 4" where appropriate) where the hydraulic oil HF is sucked in by the gear motor 5. In this case, as shown in Figure 5(c), the AC piston 32 is biased by the set spring 34 toward the suction side communication passage 4 (the lower side of the figure), thereby pressurizing the hydraulic oil HF in the suction side communication passage 4 to a predetermined pressure (for example, saturated vapor pressure) or higher and preventing it from becoming negative pressure.

[0065] As described above, the pair of accumulators 8, 8 in which the AC piston 32 operates are arranged near the gear motor 5 and on both sides thereof, so that the pressurization of the hydraulic oil HF by each accumulator 8 can be performed efficiently and in a well-balanced manner. As described above, by preventing the internal pressure of the hydraulic oil HF from becoming negative due to the operation of the gear motor 5, cavitation in the hydraulic oil HF can be prevented, and thereby problems such as noise caused by cavitation can be avoided.

[0066] In the initial state of the damper 1, the detection rod 33 of the accumulator 8 protrudes a predetermined length from the casing 31 as shown in FIG. 5(a). However, if the protruding length of the detection rod 33 is shorter than the original length in the initial state as shown in FIG. 5(c), for example, the internal pressure of the hydraulic oil HF may be lower than the original pressure. This may be due to a malfunction such as leakage of the hydraulic oil HF from the cylinder 2 or the communication passage 4. Therefore, by visually checking the change in the protruding length of the detection rod 33, it is possible to easily detect a malfunction of the damper 1.

[0067] Furthermore, in the damper 1 of this embodiment, the flywheel 6 is rotatably and firmly supported by a flywheel support device 7 provided on the peripheral wall 2a of the cylinder 2. This prevents excessive loads (radial and / or thrust loads) from acting on the output shaft (rotating shaft) 17 of the gear motor 5 when the flywheel 6 rotates. Furthermore, the flywheel support device 7 has a radial bearing 21A and a pair of thrust bearings 21B, 21B, which support the radial and thrust loads on the protruding shaft portion 20 of the flywheel 6. This significantly reduces the radial and thrust loads acting on the outer rotor 15 and inner rotor 16 of the gear motor 5 as the flywheel 6 rotates.

[0068] Next, a damper 51 according to a second embodiment of the present invention will be described with reference to Figures 8 to 10. In the following description, the same components as those of the damper 1 according to the first embodiment described above will be denoted by the same reference numerals, and detailed description thereof will be omitted.

[0069] As shown in Figure 8(c), this damper 51 is obtained by adding a damping performance adjustment mechanism 52 for adjusting damping performance to the damper 1 of the first embodiment. This damping performance adjustment mechanism (hereinafter simply referred to as the "adjustment mechanism") 52 has a pair of adjustment mechanisms 52, 52 provided on both sides of the gear motor 5 in the main passage portion 4a of the communication passage 4. Note that these adjustment mechanisms 52, 52 are illustrated symmetrically in the vertical and horizontal directions in Figures 8(a) and 8(b), but since they have substantially the same configuration, the same components will be denoted by the same reference numerals in the following description. Furthermore, when distinguishing between the adjustment mechanisms 52, 52 on the left and right sides of the gear motor 5 in Figure 8(c), they will be denoted by the reference numerals 52A and 52B, respectively.

[0070] As shown in Figure 8(a) or (b), each adjustment mechanism 52 includes a casing 53 that communicates with the communication passage 4 via two inlets and outlets 53a, 53a and has two passages (a first passage 54a and a second passage 54b) connecting the two inlets and outlets 53a, 53a, a check valve 55 provided in the first passage 54a, and an adjustment valve 56 provided in the second passage 54b.

[0071] The check valve 55 is configured as a normally closed valve and has a valve element 55a and a spring 55b that biases the valve in the closing direction. As shown in Figure 8(a), the check valve 55 of the left-side adjustment mechanism 52A is opened only when the hydraulic oil HF in the communicating passage 4 flows from the right-side gear motor 5 through the first passage 54a in the casing 53. As shown in Figure 8(b), the check valve 55 of the right-side adjustment mechanism 52B is opened only when the hydraulic oil HF in the communicating passage 4 flows from the left-side gear motor 5 through the first passage 54a in the casing 53.

[0072] On the other hand, like the check valve 55, the adjustment valve 56 is configured as a normally closed valve and includes a valve element 56a, a spring 56b that biases the valve element 56a in the valve closing direction, and an adjustment screw 56c that adjusts the biasing force of the spring 56b. By rotating the adjustment screw 56c, the biasing force of the spring 56b can be increased or decreased, and accordingly, the ease with which the hydraulic oil HF flows through the second passage 54b can be adjusted. This adjusts the damping performance of the damper 51.

[0073] 9 shows the state when the piston 3 moves toward the first fluid chamber 2e on the left side. In this case, the hydraulic oil HF in the first fluid chamber 2e is pushed out by the piston 3, flows into the communication passage 4 through the left communication port 2h, passes through the left adjustment mechanism 52A, and flows into the casing 14 of the gear motor 5. In this case, as shown in FIG. 9(a), in the left adjustment mechanism 52A, the hydraulic oil HF that flows in from the left port 53a of the casing 53 passes through the second passage 54b in which the adjustment valve 56 is provided, and flows out from the right port 53a.

[0074] Furthermore, the hydraulic oil HF flowing out from the casing 14 of the gear motor 5 passes through the right-side adjustment mechanism 52B, and flows into the second fluid chamber 2f of the cylinder 2 via the communication passage 4 and the right-side communication port 2h. In this case, as shown in FIG. 9(b), in the right-side adjustment mechanism 52B, the hydraulic oil HF flowing in from the left-side inlet / outlet 53a of the casing 53 passes through the first passage 54a in which the check valve 55 is provided, and flows out from the right-side inlet / outlet 53a.

[0075] 10 shows a state when the piston 3 moves toward the right-side second fluid chamber 2f, opposite to that shown in FIG. 9. In this case, the hydraulic oil HF in the second fluid chamber 2f is pushed out by the piston 3, flows into the communication passage 4 via the right-side communication port 2h, passes through the right-side adjustment mechanism 52B, and flows into the casing 14 of the gear motor 5. In this case, as shown in FIG. 10(b), in the right-side adjustment mechanism 52B, the hydraulic oil HF that flows in from the right-side port 53a of the casing 53 passes through the second passage 54b in which the adjustment valve 56 is provided, and flows out from the left-side port 53a.

[0076] Furthermore, the hydraulic oil HF flowing out from the casing 14 of the gear motor 5 passes through the left-side adjustment mechanism 52A, and flows into the first fluid chamber 2e of the cylinder 2 via the communication passage 4 and the left-side communication port 2h. In this case, as shown in Figure 10(a), in the left-side adjustment mechanism 52A, the hydraulic oil HF flowing in from the right-side inlet / outlet 53a of the casing 53 passes through the first passage 54a in which the check valve 55 is provided, and flows out from the left-side inlet / outlet 53a.

[0077] As described above, the damper 51 of the second embodiment can obtain the same effects as the damper 1 of the first embodiment described above, and in addition, the damping performance of the damper 51 can be easily adjusted by adjusting the flow rate of the hydraulic oil HF flowing through the connecting passage 4.

[0078] Next, a damper 61 according to a third embodiment of the present invention will be described with reference to Fig. 11. In the following description, the same components as those of the damper 1 according to the first embodiment described above will be denoted by the same reference numerals, and detailed description thereof will be omitted.

[0079] 11, this damper 61 is configured such that, from top to bottom, a flywheel support device 7B, a flywheel 6B, and a gear motor 5 are arranged below a cylinder 2B. As shown in the figure, the flywheel support device 7B rotatably supports a protruding shaft portion 20B, which is provided so as to protrude upward from the center of the top surface of the flywheel 6B, via a bearing 21D.

[0080] The protruding shaft portion 20B is composed of a cylindrical shaft body 62 that opens downward and a flange 63 that is integral with the upper end of the shaft body 62 and has a predetermined diameter larger than that of the shaft body 62. The output shaft 17 of the gear motor 5 is integrally connected to the flywheel 6B via a rotational torque transmission key 18, with the output shaft 17 passing through a central connecting hole 6a from below. The upper end of the output shaft 17 is inserted into the shaft body 62 of the protruding shaft portion 20B from below and is integrally connected to the shaft body 62 via the rotational torque transmission key 18. A bearing 21D, which is a thrust bearing, is provided between the lower surface of the flange 63 of the protruding shaft portion 20B and a bearing holder 64 that covers the flange 63 and wraps around the lower side of the flange 63. The bearing holder 64 is fixed to the lower surface of the peripheral wall 2a of the cylinder 2 with multiple bolts 28 (only two are shown in FIG. 11 ).

[0081] With the flywheel support device 7B configured as described above, the flange 63 of the protruding shaft portion 20B of the flywheel 6B is rotatably supported by the bearing 21D from below. This allows the weight of the flywheel 6B to be firmly supported even when the flywheel 6B is placed below the cylinder 2B, and also significantly reduces the thrust load acting on the gear motor 5.

[0082] Next, a damper 71 according to a fourth embodiment of the present invention will be described with reference to Figures 12 to 14. In the following description, the same components as those of the damper 1 according to the first embodiment described above will be denoted by the same reference numerals, and detailed description thereof will be omitted.

[0083] Fig. 12 shows the entire damper 71, and Fig. 13 shows an enlarged view of the gear motor 5 and flywheel 6C installed on the cylinder 2C. As shown in both figures, in this damper 71, the gear motor 5 is positioned above the cylinder 2C and the flywheel 6C is positioned in front of the gear motor 5 by a gear motor / flywheel support device 72 (pressure motor / flywheel support device).

[0084] 13(a) to 13(c), the gear motor / flywheel support device 72 is open from the top to the back, holds the gear motor 5 inside, and has a metal holder 73 at the front that rotatably supports the flywheel 6C. The holder 73 has a base portion 74 that is fixed to the outer circumferential surface of the cylinder 2C by screws or the like, and a support wall portion 75 that stands on the front end of the base portion 74, and these are integrally formed.

[0085] The support wall 75 of the holder 73 has a through-hole 75a through which the output shaft 17 of the gear motor 5 passes. The gear motor 5 is fixed to the back surface of the support wall 75 with a plurality of screws, while a bearing 21 (21E) is provided on the front surface of the support wall 75 concentrically with the through-hole 75a and between it and a central shaft 77 (described later) of the flywheel 6C. The bearing 21E is a thrust bearing.

[0086] The holder 73 also has a pair of left and right side walls 76, 76 erected on both left and right ends of the base 74, and each side wall 76 is formed with a through hole 76a through which the communication passage 4 passes.

[0087] The flywheel 6C is formed in a disk shape with a predetermined diameter and thickness, and is provided at its center with a central shaft portion 77 that protrudes in the thickness direction. The central shaft portion 77 is formed in a thick cylindrical shape, and a through hole 77a with a predetermined diameter is formed in the center.

[0088] The flywheel 6C is directly connected to the output shaft 17 of the gear motor 5 via a rotation torque transmission key (not shown) with the output shaft 17 inserted into the through hole 77a of the central shaft portion 77. This allows the output shaft 17 of the gear motor 5 and the flywheel 6C to rotate integrally.

[0089] In this embodiment, the accumulator 8 is omitted from the communication passage 4, but it goes without saying that the accumulator 8 may be provided in the communication passage 4, as in the above-described embodiments.

[0090] As described above, according to the damper 71 of the fourth embodiment, the gear motor 5 is supported by the gear motor / flywheel support device 72, and the flywheel 6C is rotatably supported. This makes it possible to stably support the gear motor 5 while preventing the gear motor 5 from being subjected to an excessive load from the flywheel 6C, thereby enabling the gear motor 5 to be used stably for a long period of time. Furthermore, in the damper 71, the center shaft 77 of the flywheel 6C is directly connected to the output shaft 17 of the gear motor 5, so the flywheel 6C and gear motor 5 can be connected without using any special connecting tool, and the gear motor 5 can efficiently rotate the flywheel 6C.

[0091] Figure 14 shows a modified example of the coupling structure between the gear motor 5 and the flywheel 6C in the fourth embodiment, similar to Figure 13. For convenience, Figures 14(b) and 14(c) show the central shaft portion 77, the output shaft 17, and a portion of their surroundings cut away, and Figure 14(c) omits the left and right side wall portions 76, 76 of the holder 73A.

[0092] In the damper 71 shown in Figure 13, the output shaft 17 of the gear motor 5 is directly connected to the central shaft 77 of the flywheel 6C, whereas in the damper 71 shown in Figure 14, the output shaft 17 of the gear motor 5 and the central shaft 77 of the flywheel 6C are coaxially connected via a shaft body 78 and a connector 79. In other words, the output shaft 17 of the gear motor 5 and the central shaft 77 of the flywheel 6C are connected with a gap between them in the front-to-rear direction (the up-and-down direction in Figure 14(a) and the left-and-right direction in Figure 14(c)).

[0093] 13, a holder 73A shown in Fig. 14 is provided with a motor support wall 81 for supporting the gear motor 5 at a predetermined position behind the support wall 75. This motor support wall 81 stands upright at a predetermined position on the base 74, and has a through-hole 81a through which the output shaft 17 of the gear motor 5 passes. The gear motor 5 is fixed to the back surface of this motor support wall 81 with a plurality of screws.

[0094] Furthermore, a bearing 21 (21F) is provided on the support wall portion 75 of the holder 73A to rotatably support the shaft main body 78. The bearing 21F is configured as a radial bearing.

[0095] A shaft body 78 having a predetermined length is inserted into and fixed to the central shaft portion 77 of the flywheel 6C through a through-hole 77a thereof. The rear end of the shaft body 78 is connected to the front end of the output shaft 17 of the gear motor 5 via a cylindrical connector 79 having a predetermined length. The shaft body 78 and the output shaft 17 are connected to each other via a rotation torque transmission key (not shown) while inserted into the connector 79.

[0096] According to the above-described modified example, the distance between the gear motor 5 and the flywheel 6C can be adjusted depending on, for example, the outer diameter and size of the cylinder 2C, the length of the central shaft portion 77 of the flywheel 6C, and the length of the output shaft 17 of the gear motor 5, and smooth rotation of the flywheel 6C by the gear motor 5 can be ensured.

[0097] The present invention is not limited to the embodiments described above and can be implemented in various forms. For example, the flywheel support device 7 of the dampers 1 and 51 of the first and second embodiments uses three bearings 21 (21A, 21B, and 21B), but the number of these bearings 21 is not particularly limited in the present invention. That is, as in the flywheel support devices 7A and 7B shown in Figures 3 and 11, respectively, it is possible to use a single bearing 21, as well as two or four or more bearings.

[0098] Furthermore, in each embodiment, the damper 1 (including 51, 61, and 71; the same applies below) is shown with the cylinder 2 (including 2A, 2B, and 2C; the same applies below) extending horizontally, but when installing the damper 1 in a structure, it is also possible to install the cylinder 2 so that it extends horizontally, or so that it extends vertically or diagonally.

[0099] Furthermore, in the first to third embodiments, in order to detect the state of the hydraulic oil HF in the damper 1, the left and right accumulators 8, 8 are provided with detection rods 33 integral with the AC pistons 32, but instead of the detection rods 33, for example, a pressure sensor may be installed in the cylinder 2 or the communication passage 4 so that the internal pressure of the hydraulic oil HF can be detected from the outside. Also, in the present embodiments, a gear motor (internal type, external type) is exemplified as the pressure motor, but it is of course possible to use pressure motors other than gear motors, such as vane motors and piston motors.

[0100] 8, the left and right adjustment mechanisms 52A and 52B for adjusting the damping performance are provided with adjustment valves 56, 56, respectively, but as shown in Figures 15(a) and 15(b), for example, the adjustment valves 56, 56 may be omitted and the diameter of the orifice 58 may be adjusted instead. In this case, the damping effect can be increased by reducing the diameter of the orifice 58.

[0101] Furthermore, the detailed configuration of the damper 1 shown in the embodiment is merely an example and can be modified as appropriate within the scope of the spirit of the present invention. [Explanation of symbols]

[0102] 1 Damper 2 cylinders 2A cylinder 2B cylinder 2C cylinder 2a Cylinder peripheral wall 2e 1st fluid chamber 2f 2nd fluid chamber 3 pistons 4 passages 5 Gear motor (pressure motor) 6 Flywheel 6A Flywheel 6B flywheel 6C flywheel 7 Flywheel support device 7A Flywheel support device 7B Flywheel support device 8 Accumulator 14 Gear motor casing 15 outer rotor 16 Inner rotor (rotating body) 17 Output shaft 20 Protruding shaft part 20A protruding shaft part 20B Protruding shaft part 20a shaft body 20b Upper flange 20c bottom flange 21 Bearings 21A Radial Bearing 21B thrust bearing 21C Radial Bearing 21D thrust bearing 21E Thrust Bearing 22 Bearing holder 27 Bearing holder (bearing holding part) 32 Accumulator piston 33 Detection rod 34 set springs 35 Stopper 51 Damper 52 Damping performance adjustment mechanism 55 Check valve 56 Regulating valve 56c Adjustment screw 58 Orifice 61 Damper 62 Shaft body 63 flange 64 Bearing holder 71 Damper 72 Gear motor flywheel support device 73 Holder 73A Holder 74 Base 75 Support wall section 77 Center shaft part 78 Shaft body 79 Connector 81 Motor support wall HF hydraulic oil (working fluid)

Claims

1. a cylinder filled with a working fluid; a piston slidably disposed within the cylinder, the piston dividing the interior of the cylinder into a first fluid chamber and a second fluid chamber; a communication passage that bypasses the piston and communicates the first fluid chamber with the second fluid chamber; a pressure motor that is disposed in the communication passage and has a rotor that is rotatably housed in a casing that communicates with the communication passage, and that converts the flow of working fluid that accompanies the sliding of the piston into rotational motion of the rotor; a flywheel disposed between the pressure motor and the cylinder and coaxially connected to the rotor; a flywheel support device provided on an outer peripheral surface of the cylinder and supporting the flywheel rotatably about an axis extending in a radial direction of the cylinder; Equipped with The flywheel is provided with a protruding shaft portion that protrudes from the center thereof toward the cylinder, The flywheel support device is a bearing that rotatably supports the protruding shaft portion; a bearing holder that holds the bearing on the outer circumferential surface of the cylinder; A damper using a pressure motor, comprising:

2. The protruding shaft portion is a shaft body having a predetermined diameter; a flange provided at an end of the shaft body on the cylinder side, the flange having a diameter larger than that of the shaft body; It has The bearing is a radial bearing fitted onto the flange; a pair of thrust bearings provided in a state in which the flange is sandwiched from one surface side and the other surface side; 2. The damper using a pressure motor according to claim 1, further comprising:

3. The protruding shaft portion has a predetermined diameter, 2. The damper using a pressure motor according to claim 1, wherein the bearing comprises a radial bearing fitted onto the protruding shaft portion.

4. The cylinder is arranged to extend horizontally, The flywheel is disposed below the cylinder, The protruding shaft portion is a shaft body having a predetermined diameter; a flange provided at an end of the shaft body on the cylinder side, the flange having a diameter larger than a diameter of the shaft body, 2. A damper using a pressure motor according to claim 1, wherein the bearing has a thrust bearing that rotatably supports the flange while supporting it from below.

5. the compressor further includes an accumulator that is provided in communication with the communication passage, stores pressure of the working fluid in order to prevent cavitation in the working fluid, and pressurizes the working fluid with the stored pressure, The accumulator comprises: a casing communicating with the communication passage; an accumulator piston slidably provided within the casing; a spring that biases the accumulator piston toward the communication passage; a detection rod that is integral with the accumulator piston, extends along the sliding direction of the accumulator piston, and protrudes from the casing to the outside, for detecting the pressure state of the working fluid; and 5. The damper using a pressure motor according to claim 1, further comprising:

6. 6. The damper using a pressure motor according to claim 5, wherein a stopper is provided inside the casing, against which the accumulator piston pressed by the working fluid in an initial state in which the working fluid has a predetermined internal pressure comes into contact against the biasing force of the spring, thereby preventing further movement.

7. 7. A damper using a pressure motor according to claim 1, further comprising a damping performance adjustment mechanism provided in the communication passage for adjusting the degree of flow of the working fluid flowing through the communication passage, thereby adjusting the damping performance of the damper.

8. a cylinder filled with a working fluid; a piston slidably disposed within the cylinder, the piston dividing the interior of the cylinder into a first fluid chamber and a second fluid chamber; a communication passage that bypasses the piston and communicates the first fluid chamber with the second fluid chamber; a pressure motor that is disposed in the communication passage and has a rotor that is rotatably housed in a casing that communicates with the communication passage, and that converts the flow of working fluid that accompanies the sliding of the piston into rotational motion of the rotor; a flywheel coaxially connected to the rotor; a pressure motor / flywheel support device that is fixed on the outer peripheral surface of the cylinder, supports the pressure motor, and directly and rotatably supports the flywheel; A damper using a pressure motor, comprising:

9. the pressure motor is configured to be rotatable integrally with the rotating body and further includes an output shaft protruding from the casing to the outside, The flywheel has a central shaft portion provided at its center, The pressure motor flywheel support device is a holder having a base portion fixed onto an outer peripheral surface of the cylinder and a support wall portion provided on the base portion; a bearing provided on the support wall of the holder and rotatably supporting the central shaft of the flywheel; It has 9. The damper using a pressure motor according to claim 8, wherein the central shaft portion of the flywheel and the output shaft of the pressure motor are coaxially connected.

10. 10. The damper using a pressure motor according to claim 9, wherein the central shaft portion of the flywheel and the output shaft of the pressure motor are directly connected.

11. The damper using a pressure motor according to claim 9, characterized in that the central shaft portion of the flywheel and the output shaft of the pressure motor are connected to each other via a predetermined connecting device while being spaced apart from each other.

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