Method for evaluating the integrity of a hydraulic motor-driven rotational inertia mass damper

Abstract

This invention provides a method for evaluating the integrity of a hydraulic motor-type rotational inertia mass damper, which allows for easy and appropriate evaluation of the integrity of the hydraulic motor-type rotational inertia mass damper. [Solution] The present invention provides a mass damper 1 (rotational inertia mass damper) having a cylinder 2 filled with hydraulic fluid HF, a piston 3 slidably provided inside the cylinder 2, a communication passage 4 that bypasses the piston 3 and communicates with the first and second oil chambers 2f and 2g, a gear motor 5 arranged in the communication passage 4, and a rotating mass 9 connected to the gear motor 5. Torque is applied to the rotating mass 9 to rotate it, and the rotation of the rotating mass 9 is converted into pressure of the hydraulic fluid HF by the gear motor 5 to move the piston 3. The torque T applied to the rotating mass 9 and the damper force FD generated in the mass damper 1 are detected during this damper driving process, and the mass damper 1 is evaluated as being in good condition when a predetermined proportional relationship is established between the detected torque T and the damper force FD.

Description

Technical Field

[0001] The present invention relates to a method for evaluating the soundness of a hydraulic motor type rotational inertia mass damper that suppresses vibration by converting the vibration of a structure or the like into the rotation of a rotating mass by a hydraulic motor.

Background Art

[0002] The applicant of the present application has disclosed a hydraulic motor type rotational inertia mass damper as described above in, for example, Patent Document 1. This rotational inertia mass damper (hereinafter referred to as "mass damper") uses a gear motor as a hydraulic motor, is filled with hydraulic oil, and includes a cylinder connected to a first part of a structure, a piston slidably provided in the cylinder, partitioning the inside of the cylinder into first and second oil chambers, and connected to a second part of the structure, a communication passage bypassing the piston and communicating with the first and second oil chambers, a hydraulic motor disposed in the communication passage, and a rotating mass connected to the hydraulic motor. In this configuration, when the structure vibrates, as the piston slides in the cylinder according to the relative displacement between the first and second parts, the hydraulic oil flows from the first or second oil chamber into the communication passage, and the pressure of the hydraulic oil due to the flow is converted into the rotational motion of the pressure motor, and the rotating mass rotates, thereby exerting a vibration suppressing effect on the structure.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] The hydraulic mass damper with the configuration described above has no track record of being used in buildings or civil engineering structures. Therefore, when selling hydraulic mass dampers, building owners and designers sometimes ask for explanations on how to verify the soundness of the hydraulic mass damper (that the damper is functioning correctly) other than the absence of oil leaks. However, currently, there is no established method for evaluating soundness, and it is not possible to provide a clear explanation to building owners and others.

[0005] The present invention was made to solve the above-mentioned problems, and aims to provide a method for evaluating the integrity of a hydraulic motor-type rotational inertia mass damper that allows for easy and appropriate evaluation of the integrity of the hydraulic motor-type rotational inertia mass damper, other than the absence of oil leakage, while the damper remains installed. [Means for solving the problem]

[0006] To achieve this objective, the method for evaluating the soundness of a hydraulic motor-type rotational inertia mass damper according to claim 1 is a hydraulic motor-type rotational inertia mass damper having a cylinder filled with hydraulic fluid, a piston slidably provided inside the cylinder and dividing the inside of the cylinder into a first oil chamber and a second oil chamber, a communication passage that bypasses the piston and communicates with the first and second oil chambers, a hydraulic motor arranged in the communication passage, and a rotating mass connected to the hydraulic motor, characterized in that the method comprises: a damper driving step in which torque is applied to the rotating mass to rotate the rotating mass and the rotation of the rotating mass is converted into hydraulic fluid pressure by the hydraulic motor to move the piston; a torque detection step in which torque applied to the rotating mass is detected during the damper driving step; a damper force detection step in which damper force generated in the rotational inertia mass damper during the damper driving step; and an evaluation step in which the rotational inertia mass damper is evaluated as sound when a predetermined proportional relationship is established between the detected torque of the rotating mass and the damper force.

[0007] This invention relates to a method for evaluating the integrity of a hydraulic motor-type rotational inertia mass damper (hereinafter referred to as "mass damper"). In this mass damper, as the piston in the cylinder slides, the hydraulic fluid flows from the first or second oil chamber to the communication passage and the hydraulic motor. The pressure of the hydraulic fluid due to this flow is converted into rotational motion of the hydraulic motor, which rotates the rotating mass, thereby exhibiting a rotational inertia mass effect (inertial force). In addition, a viscous damping effect (viscous force) is exhibited by the hydraulic fluid as it flows through the communication passage and inside the hydraulic motor, and together with the rotational inertia mass effect, a vibration suppression effect is exhibited.

[0008] According to the present invention, in order to evaluate the integrity of such a mass damper, torque is applied to a rotating mass to forcibly rotate it, and the rotation of the rotating mass is converted into hydraulic fluid pressure by a hydraulic motor to move a piston (damper driving process). In addition, the torque applied to the rotating mass and the damper force generated in the mass damper are detected during the damper driving process (torque detection process, damper force detection process). As will be described later, a proportional relationship is established between the torque obtained in the damper driving process and the damper force, as long as the mass damper is functioning normally. From this viewpoint, when a predetermined proportional relationship is established between the detected torque of the rotating mass and the damper force, the rotational inertia mass damper is evaluated as functioning normally and being in good condition (evaluation process). This makes it possible to easily and appropriately evaluate the integrity of a hydraulic motor-type mass damper while the damper is still installed. In this specification, "detection" includes not only cases where data values ​​representing an event are directly measured using measuring instruments, but also cases where they are calculated from measurement results, etc.

[0009] The invention according to claim 2 is a method for evaluating the integrity of a hydraulic motor-type rotational inertia mass damper as described in claim 1, characterized in that, in the damper driving step, torque is applied to the rotating mass by a spring scale hooked into a hole formed in the rotating mass, and the reaction force from the rotating mass at this time is measured, and in the torque detection step, torque is detected based on the force measured by the spring scale and the distance from the center of the rotating mass to the hole.

[0010] In this configuration, a spring scale attached to a hole formed in the rotating mass applies torque to the rotating mass, and the reaction force is measured. Then, the torque is detected based on the measured force and the distance from the center of the rotating mass to the hole. In this way, the application of torque to the rotating mass and the measurement of the reaction force for torque detection can be performed simply and reliably by using a spring scale.

[0011] The invention according to claim 3 is a method for evaluating the integrity of a hydraulic motor-type rotational inertia mass damper as described in claim 1, characterized in that, in the damper force detection step, the pressures on both sides of the hydraulic motor in the communication passage are measured as first and second pressures, respectively, and the damper force is detected based on the difference between the measured first and second pressures and the cross-sectional area of ​​the piston.

[0012] With this configuration, the pressure (first and second pressures) on both sides of the hydraulic motor in the communication passage can be measured, and the damper force can be easily detected based on the difference between the measured first and second pressures and the cross-sectional area of ​​the piston.

[0013] The invention according to claim 4 is a method for evaluating the integrity of a hydraulic motor-type rotational inertia mass damper according to claim 1 as described in claim 3, characterized in that first and second hydraulic couplers for air bleeding are provided on both sides of the hydraulic motor in the communication passage, and in the damper force detection step, first and second pressure gauges are attached to the first and second hydraulic couplers, respectively, and the first and second pressures are measured using the first and second pressure gauges.

[0014] In this configuration, the first and second pressures are measured by first and second pressure gauges attached to first and second hydraulic couplers provided on both sides of the hydraulic motor in the communication passage. This allows the first and second pressure gauges to be attached and detached, and the first and second pressures to be measured, while utilizing the first and second hydraulic couplers, which are originally provided for air bleeding, with virtually no air contamination or oil leakage.

[0015] The invention according to claim 5 is a method for evaluating the integrity of a hydraulic motor-type rotational inertia mass damper as described in claim 1, characterized in that, in the evaluation step, the ratio of the detected torque of the rotating mass to the damper force is compared with a predetermined reference ratio that should be obtained when the rotational inertia mass damper is in a healthy state, and the rotational inertia mass damper is evaluated as healthy when the degree of deviation between the two is small.

[0016] With this configuration, when the degree of deviation between the detected ratio of torque to damper force of the rotating mass and a predetermined reference ratio that should be obtained when the rotational inertia mass damper is in a healthy state is small, it can be appropriately evaluated that the rotational inertia mass damper is healthy, as it indicates that the proportional relationship between torque to damper force of the rotating mass is maintained.

[0017] The invention according to claim 6 is a method for evaluating the integrity of a hydraulic motor-type rotational inertia mass damper according to any one of claims 1 to 5, wherein the rotational inertia mass damper further comprises a drain pipe connected to the drain passage of a hydraulic motor, an accumulator provided inside a piston rod integrated with the piston and connected to the drain pipe, which stores a portion of the pressure of the hydraulic motor, and a third hydraulic coupler provided in the drain passage, and further comprises a second evaluation step of attaching a third pressure gauge to the third hydraulic coupler and evaluating the integrity of the drain pressure of the hydraulic motor and the accumulator based on the third pressure measured by the third pressure gauge.

[0018] With this configuration, the third pressure is measured by a third pressure gauge attached to a third hydraulic coupler installed in the drain passage of the hydraulic motor. Based on the measured third pressure, the drain pressure of the hydraulic motor and the health of the accumulator can be appropriately evaluated by comparing it with, for example, the pressure measured when the rotational inertia mass damper is in a healthy state. Furthermore, the third pressure gauge can be attached and detached, and the third pressure measured, while utilizing the third hydraulic coupler that is originally installed in the drain passage of the hydraulic motor, with virtually no air contamination or oil leakage. [Brief explanation of the drawing]

[0019] [Figure 1] A longitudinal sectional view showing a partial cutout of a hydraulic motor type rotational inertia mass damper to which the present invention is applied. [Figure 2] A longitudinal sectional view showing a state in which torque is applied to the flywheel and the first and second pressures are measured by the first and second pressure gauges in the rotational inertia mass damper of FIG. 1. [Figure 3] A flowchart showing a process (procedure) for evaluating the soundness of the rotational inertia mass damper of FIG. 1. [Figure 4] A longitudinal sectional view showing a state in which the third pressure is measured by the third pressure gauge in the rotational inertia mass damper of FIG. 1 in order to evaluate the soundness of the drain pressure and the accumulator.

Mode for Carrying Out the Invention

[0020] Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the drawings. First, a hydraulic rotational inertia mass damper (hereinafter referred to as "mass damper") to which the present invention is applied will be described. As shown in FIG. 1, the mass damper 1 includes a cylinder 2, a piston 3 slidably provided in the cylinder 2, a reverse U-shaped communication passage 4 that bypasses the piston 3 and communicates with the inside of the cylinder 2, a gear motor 5 serving as a hydraulic motor disposed in the communication passage 4, and a flywheel 9 connected to the output shaft 8 of the gear motor 5. The communication passage 4 is composed of a pair of vertical portions 4a, 4a that communicate with the first and second oil chambers 2f, 2g of the cylinder 2, and a horizontal portion 4b that connects between the upper end portions of the vertical portions 4a, 4a.

[0021] The cylinder 2 integrally has a cylindrical peripheral wall 2a and first and second end walls 2b, 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. The central portion in the axial direction of the peripheral wall 2a is a rod fitting portion 2d having a large wall thickness (small inner diameter), and the space between the rod fitting portion 2d and the second end wall 2c is a rod accommodating portion 2e. A second fixture FL2 is provided on the second end wall 2c via a ball joint BJ.

[0022] The piston 3 is provided axially slidably within the cylinder 2, partitioning the internal space of the cylinder 2 into a first oil chamber 2f and a second oil chamber 2g. The first and second oil chambers 2f, 2g and the communication passage 4 are filled with hydraulic fluid HF. The hydraulic fluid HF is a normal one having appropriate viscosity.

[0023] A piston rod 10 is provided concentrically and integrally on the piston 3. The piston rod 10 is composed of a first rod portion 10a extending from the piston 3 to one side in the axial direction (the left side in FIG. 1) and a second rod portion 10b extending to the other side (the right side in FIG. 1). The first rod portion 10a penetrates the first end wall 2b in a liquid-tight manner and is supported thereby, partially protruding outside the cylinder 2. A first fixture FL1 is provided at the tip of the first rod portion 10a via a ball joint BJ. The second rod portion 10b is supported by being liquid-tightly fitted into the rod fitting portion 2d of the cylinder 2 and is partially accommodated in the rod accommodation portion 2e.

[0024] An accumulator 21 is provided on the second rod portion 10b to accommodate a part of the pressure in the cylinder 2 that has increased due to temperature expansion of the hydraulic fluid HF. The accumulator 21 has a hollow casing portion 22 formed in approximately two-thirds of the range on the tip side of the second rod portion 10b, a piston 24 provided slidably within the casing portion 22 and defining a pressure accumulation chamber 23 on the piston 3 side, and a set spring 25 biasing the piston 24 toward the pressure accumulation chamber 23 side. Further, a rod communication hole 10c is formed coaxially on the second rod portion 10b. The rod communication hole 10c communicates with the pressure accumulation chamber 23 at one end and with the piston communication hole 3a of the piston 3 at the other end.

[0025] On the other hand, the piston 3 has first and second communication holes that penetrate axially and communicate with the first and second oil chambers 2f and 2g, a third communication hole that extends vertically to connect the first and second communication holes, and a piston communication hole 3a that extends from the center of the third communication hole to penetrate on both sides in the axial direction and communicates with the rod communication hole 10c. Check valves 26, 26 are provided on both sides of the third communication hole in the first communication hole. Each check valve 26 is configured to allow the flow of hydraulic fluid HF only from the third communication hole side to the first or second oil chamber 2f and 2g side. In addition, orifices 27, 27 are provided on both sides of the third communication hole in the second communication hole.

[0026] In the above configuration, when the pressure inside the cylinder 2 increases due to the temperature rise of the hydraulic fluid HF, the hydraulic fluid HF slowly flows from the first and second oil chambers 2f and 2g into the accumulator chamber 23 of the accumulator 21 via the second communication hole of the piston 3, the orifices 27, 27, the third communication hole, the piston communication hole 3a, and the rod communication hole 10c. As a result, the set spring 25 is compressed via the piston 24, and a portion of the pressure in the first and second oil chambers 2f and 2g is stored in the accumulator 21, thereby preventing malfunctions caused by pressure increases due to the temperature rise of the hydraulic fluid HF.

[0027] From this state, when the temperature of the hydraulic oil HF decreases, the hydraulic oil HF in the accumulator chamber 23 is returned to the first and second oil chambers 2f and 2g through the rod communication hole 10c, the piston communication hole 3a, the third communication hole, the opened check valves 26, 26, and the first communication hole, thereby releasing the pressure stored in the accumulator 21 and returning to its original state.

[0028] Furthermore, the piston 3 has a first relief passage 3b and a second relief passage 3c that penetrate in the axial direction. The first and second relief passages 3b and 3c are provided with a first relief valve 11 and a second relief valve 12, respectively. The first and second relief valves 11 and 12 have the same configuration as each other and are configured as normally closed valves, and each has a valve body and a spring that biases the valve body in the closing direction.

[0029] The first relief valve 11 closes the first communication passage 3b until the pressure of the hydraulic fluid HF in the first oil chamber 2f reaches a predetermined pressure, and then opens the first communication passage 3b when the predetermined pressure is reached. As a result, the pressure in the first oil chamber 2f is released to the second oil chamber 2g side via the first communication passage 3b and limited to below the predetermined pressure. Similarly, the second relief valve 12 closes the second communication passage 3c until the pressure in the second oil chamber 2g reaches a predetermined pressure, and then opens the second communication passage 3c when the predetermined pressure is reached. As a result, the pressure in the second oil chamber 2g is released to the first oil chamber 2f side via the second communication passage 3c and limited to below the predetermined pressure.

[0030] The gear motor 5 is, for example, an internally geared type and is positioned in the horizontal section 4b 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 an output gear (neither shown) housed in the housing 6 and meshing with each other, and an output shaft 8 integrally provided with the output gear. The housing 6 is supported by the peripheral wall 2a of the cylinder 2. A drain passage (not shown) for discharging the hydraulic fluid HF is also provided inside the housing 6. The output shaft 8 is liquid-tightly supported by the housing 6 via a seal (not shown). Note that an externally geared type may be used instead of the internally geared type for the gear motor 5.

[0031] The flywheel 9 is made of a material with a relatively high specific gravity, such as steel, and is formed, for example, in the shape of a disc, and is integrally mounted coaxially with the output shaft 8. The flywheel 9 also has four holes 9a for attaching a spring scale, which will be described later, and are formed at positions that are equidistant from each other from the center of rotation and equally spaced in the circumferential direction.

[0032] The mass damper 1 also includes a drain hose 61 for discharging hydraulic fluid HF from the housing 6. The drain hose 61 is flexible, with one end connected to the drain passage of the housing 6 and the other end connected to the first rod portion 10a of the piston rod 10, and is installed in a loose manner overall. More specifically, the other end of the drain hose 61 is connected to a second rod communication hole 10d formed in the first rod portion 10a. The second rod communication hole 10d opens at one end to the outer circumferential surface of the first rod portion 10a, extends coaxially with the first rod portion 10a, and communicates with the piston communication hole 3a at the other end. In addition, a check valve 62 is provided at the other end of the drain hose 61, which allows only the flow of hydraulic fluid HF and air from the housing 6 to the piston rod 10 side.

[0033] Furthermore, as a configuration for bleeding air from the mass damper 1, first and second hydraulic couplers 63 and 64 are provided at the left and right ends of the horizontal section 4b of the connecting passage 4 (the upper ends of each vertical section 4a), and a third hydraulic coupler 65 is provided in the drain passage of the housing 6. These hydraulic couplers 63 to 65 are paired with hose-side couplers (none of which are shown) to which hydraulic hoses are connected, and have the function of opening (valving) the passage when the hose-side coupler is attached and closing (valving) the passage when the hose-side coupler is removed (automatic opening and closing function). In addition, because the connection surfaces of the hydraulic couplers 63 to 65 and the hose-side coupler are flat, the ingress of air into the interior during installation and the leakage of liquid to the outside during removal are minimized.

[0034] Furthermore, as hydraulic hoses connected to the hose-side coupler, there are press-in hoses connected to the hydraulic oil tank and pump (neither shown) for pressurizing the hydraulic oil HF into the mass damper 1, and open hoses that are open to the outside for discharging the hydraulic oil HF and air from the mass damper 1. Based on the above configuration, the first to third hydraulic couplers 63 to 65 are each set to one of the following three modes depending on whether the hose-side coupler is connected (attached or detached) and the type of hydraulic hose. A. Closed mode where the hose-side coupler is not connected and the connection is closed. B. Press-fit mode in which the press-fit hose is connected via the hose-side coupler and the hydraulic fluid HF is press-fitted. C. The discharge hose is connected via the hose-side coupler and is open to the outside in open mode.

[0035] In Figure 1, reference numeral 51 denotes a hydraulic fluid injection hole formed in the rod fitting portion 2d of the cylinder 2 for injecting hydraulic fluid HF into the second oil chamber 2g, and reference numeral 52 denotes a check valve for preventing backflow provided near the inlet of the hydraulic fluid injection hole 51. Reference numerals 53, 53 denotes a base provided on the cylinder 2 to prevent the mass damper 1 from rotating or tipping over.

[0036] The mass damper 1, configured as described above, is installed, for example, between two relatively displaced parts within a structure (e.g., an upper beam and a lower beam) via first and second mounting fixtures FL1 and FL2, and is used as a seismic damping device. The operation of the mass damper 1 will be described below.

[0037] Figure 1 shows the initial state of the mass damper 1. When the structure vibrates, such as during an earthquake, the piston 3 reciprocates within the cylinder 2 in accordance with the relative displacement between the two parts to which the mass damper 1 is attached. Consequently, the hydraulic fluid HF in the first or second oil chambers 2f and 2g is pushed out by the piston 3 and flows into the communication passage 4, flows through the housing 6 of the gear motor 5, and then flows into the second or first oil chambers 2g and 2f.

[0038] The pressure generated by the flow of the hydraulic fluid HF is converted into rotational motion of the input and output gears of the gear motor 5, and the flywheel 9, which is integrated with the output shaft 8, is rotated, thereby exerting a rotational inertia mass effect (inertial force). In addition, the viscous damping effect (viscous force) due to the flow resistance as the hydraulic fluid HF flows through the communication passage 4 and the inside of the gear motor 5 is exerted, and together with the rotational inertia mass effect, a vibration suppression effect on the structure is achieved.

[0039] Furthermore, if the pressure inside the housing 6 rises due to the operation of the mass damper 1 and gear motor 5 for a long period of time in response to a long-period seismic input, for example, and becomes greater than the pressure in the accumulator chamber 23 of the accumulator 21, the check valve 62 opens. As a result, a portion of the hydraulic fluid HF inside the housing 6 is discharged into the accumulator chamber 23 of the accumulator 21 via the drain passage, drain hose 61, second rod communication hole 10d, piston communication hole 3a, and rod communication hole 10c inside the housing 6. Consequently, the pressure inside the housing 6 is released into the accumulator 21, preventing the housing 6 from becoming excessively high.

[0040] Furthermore, according to the mass damper 1 of this embodiment, by switching the modes of the first to third hydraulic couplers 63 to 65 between closed mode, press-fit mode, or open mode, hydraulic fluid HF is press-injected into the drain passage of the housing 6 via these hydraulic couplers 63 to 65, and air is discharged together with the hydraulic fluid HF from the gear motor 5, drain passage, and connecting passage 4, thereby effectively removing air from the hydraulic fluid HF piping and the like.

[0041] Next, the method for evaluating the integrity of the mass damper 1 according to the present invention will be described with reference to Figures 2 and 3. Figure 3 is a flowchart of the process (procedure). First, in step 1 (illustrated as "S1", the same applies hereinafter), the mass damper 1 is forcibly driven (damper driving step). Specifically, as shown in Figure 2 for example, the spring hook of a spring scale (not shown) is hooked into one of the four holes 9a formed in the flywheel 9, and the spring scale is pulled down as indicated by the arrow. As a result, the flywheel 9 rotates clockwise in the figure, and this rotation is converted into the flow of hydraulic fluid HF in the communication passage 4 by the gear motor 5, which presses the piston 3, causing the piston 3 to move in one direction and drive the mass damper 1.

[0042] Next, in step 2, the torque T acting on the flywheel 9 during the damper drive process is calculated via a spring scale (torque detection process). Specifically, for example, the torque T is calculated using the spring scale measurement (force F) and the distance L from the rotation center of the flywheel 9 to the hole 9a (arm length) by the following equation (1). Torque T = Force F × Arm length L ···(1)

[0043] Next, in step 3, the damper force FD generated in the mass damper 1 during the damper driving process is calculated (damper force detection process). Specifically, as shown in Figure 2, for example, first and second pressure gauges 71 and 72 are attached to the first and second hydraulic couplers 63 and 64, respectively, via hose-side couplers, and the first and second pressures P1 and P2 are measured. Then, using the measured first and second pressures P1 and P2 and the piston cross-sectional area AP, the damper force FD is calculated by the following equation (2). Damper force FD = |First pressure P1 - Second pressure P2| × Piston cross-sectional area Ap ···(2)

[0044] Next, in step 4 and beyond, the soundness of the mass damper 1 is evaluated using the calculated torque T and damper force FD (evaluation process). First, in step 4, the ratio of torque T to damper force FD (torque / damper force ratio) T / FD is calculated, and it is determined whether or not the following equation (3) is true. (T0 / FD0)-α ≦ T / FD ≦ (T0 / FD0)+α ···(3) Here, T0 and FD0 are the torque and damper force calculated using the same method as in steps 2 and 3 above when the mass damper 1 is in a healthy state, for example, at the time of shipment, and T0 / FD0 is the ratio of the two (reference ratio). Also, α is the allowable change in the torque / damper force ratio T / FD from the time of shipment, and is set to a relatively small predetermined value.

[0045] The technical significance of the discriminant equation (3) above will now be explained. As described above, if a torque T is applied to the flywheel 9 of the mass damper 1, and a damper force FD is generated as a result, then the amount of work Wt due to the torque T and the amount of work Wd due to the damper force FD when the flywheel 9 rotates once can be expressed as shown in the following equations (4) and (5). Wt = T × 2π ···(4) Wd = FD × [Motor extrusion volume Vm / Piston cross-sectional area Ap] × Torque efficiency Et ...(5) Here, torque efficiency Et is the efficiency of converting damper force FD into torque T.

[0046] Since the work Wt and Wd in equations (4) and (5) are equal, equation (6) holds. Furthermore, by rearranging equation (6), we obtain equation (7). T × 2π = FD × [Vm / Ap] × Et (6) T / FD = (1 / 2π) × [Vm / Ap] × Et ···(7) In equation (7), the motor extrusion volume Vm and piston cross-sectional area Ap on the right-hand side are constants for a single damper, and the torque efficiency Et is approximately constant when mass damper 1 is operating normally. Therefore, as long as mass damper 1 is operating normally, the torque / damper force ratio T / FD on the left-hand side of equation (7) is approximately constant, and a proportional relationship exists between torque T and damper force FD. Furthermore, when the volumetric efficiency Ev and torque efficiency Et are in an ideal state (Ev=1, Et=1), the equivalent mass M due to the rotational moment of inertia of the flywheel 9 (outer diameter RD, actual mass m) of the mass damper 1 can be expressed by the following equation (8). M = [(2π×Ap) / Vm] 2 × (m × RD 2 ) / 8 ···(8) From equation (8), the equivalent mass M of the flywheel 9 of the mass damper 1 due to its rotational inertia moment is expressed as a function of the motor extrusion volume Vm and the piston cross-sectional area Ap, similar to equation (7). Therefore, by evaluating it using the discriminant equation (3), if the result is Yes, it can be evaluated that the equivalent mass M due to the rotational inertia moment of the flywheel 9 is also at a healthy value.

[0047] The above discriminant formula (3) is based on the technical considerations described above. Therefore, when the discriminant result in step 4 is YES and the torque / damper force ratio T / FD is within the predetermined range defined by formula (3), it is determined that the torque / damper force ratio T / FD has hardly changed from the reference time and that the proportional relationship between torque T and damper force FD is maintained, and the mass damper 1 is evaluated as being in good condition (step 5), and the evaluation process is completed.

[0048] On the other hand, if the result of Step 4 is NO, and the torque / damper force ratio T / FD is not within the specified range, it is determined that the torque / damper force ratio T / FD has changed relatively significantly from the reference value, and the proportional relationship between torque T and damper force FD is not maintained. Therefore, the mass damper 1 is evaluated as not being in good condition (Step 6), and the evaluation process is terminated.

[0049] As described above, according to this embodiment, by applying torque to the flywheel 9, the flywheel 9 is forcibly rotated, and the rotation of the flywheel 9 is converted into pressure of the hydraulic fluid HF by the gear motor 5, which moves the piston 3. Furthermore, the torque T applied to the flywheel 9 during this damper driving process and the damper force FD generated in the mass damper 1 are calculated (steps 2 and 3 in Figure 3). When a predetermined proportional relationship is established between the calculated torque T and the damper force FD, the mass damper 1 is evaluated as operating normally and being in good condition (steps 4 to 6). This makes it possible to easily and appropriately evaluate the condition of the hydraulic motor type mass damper 1, other than the absence of oil leakage, while the mass damper 1 remains installed.

[0050] Furthermore, a spring scale attached to a hole 9a formed in the flywheel 9 is used to apply torque to the flywheel 9, and the reaction force is measured. Then, the torque T is calculated based on the measured force F and the distance L from the center of the flywheel 9 to the hole 9a. In this way, the application of torque to the flywheel 9 and the measurement of the force F for calculating the torque T can be performed simply and reliably by using a spring scale.

[0051] Furthermore, the pressures on both sides of the gear motor 5 in the connecting passage 4 are measured as first and second pressures P1 and P2, and the damper force FD can be easily calculated based on the difference between the measured first and second pressures P1 and P2 and the piston cross-sectional area Ap. In addition, the first and second pressures P1 and P2 are measured by first and second pressure gauges 71 and 72 attached to first and second hydraulic couplers 63 and 64 provided on both sides of the gear motor 5 in the connecting passage 4. This allows the first and second pressure gauges 71 and 72 to be attached and detached, and the first and second pressures P1 and P2 to be measured, with minimal air contamination or oil leakage, by utilizing the first and second hydraulic couplers 63 and 64, which are originally provided for air bleeding.

[0052] Furthermore, when the difference (degree of deviation) between the calculated torque / damper force ratio T / FD and a predetermined reference ratio T0 / FD0 that should be obtained when the mass damper 1 is in a healthy state is small, it can be assumed that the proportional relationship between the torque T of the flywheel 9 and the damper force FD is maintained, and the mass damper 1 can be appropriately evaluated as being in a healthy state.

[0053] Next, with reference to Figure 4, the method for evaluating the drain pressure of the gear motor 5 and the integrity of the accumulator 21 will be explained. As shown in the figure, in this evaluation method, a third pressure gauge 81 is attached to the third hydraulic coupler 65 via a hose-side coupler, and the third pressure P3 is measured. The measured third pressure P3 is then compared with a reference pressure, for example, the pressure measured by the same method at the time of shipment of the mass damper 1.

[0054] As a result, when the difference between the reference pressure and the third pressure is relatively small, the drain pressure of the gear motor 5 and the pressure of the accumulator 21 are considered to be maintained with little to no leakage, and the drain pressure and accumulator 21 are evaluated as being healthy. On the other hand, when the difference between the reference pressure and the third pressure is relatively large, the drain pressure and the pressure of the accumulator 21 are considered to have leaked and decreased significantly, and the drain pressure and accumulator 21 are evaluated as being unhealthy.

[0055] As described above, the third pressure P3 is measured by the third pressure gauge 81 attached to the third hydraulic coupler 65 provided in the drain passage of the gear motor 5. Based on the measured third pressure P3, the drain pressure of the gear motor 5 and the integrity of the accumulator 21 can be appropriately evaluated by comparing the third pressure with, for example, the reference pressure measured when the rotational inertia mass damper is in a healthy state. Furthermore, the third pressure gauge 81 can be attached and detached, and the third pressure P3 can be measured, while utilizing the third hydraulic coupler 65 that is originally provided in the drain passage of the gear motor 5, with virtually no air contamination or oil leakage.

[0056] It should be noted that the present invention is not limited to the embodiments described and can be implemented in various ways. For example, in the embodiments, both the application of torque to the flywheel 9 and the measurement of the force F for calculating the torque T are performed using a spring scale, but one or both of these may be performed by other suitable means. Also, instead of calculating the torque T by multiplying the measured force F by the arm length L, the torque T may be detected by directly measuring it using a suitable torque sensor.

[0057] In this embodiment, a torque is applied to the flywheel 9 in one direction, and the first and second pressures P1 and P2 are measured at that time. However, a torque in the opposite direction may then be applied, and the first and second pressures P1 and P2 may be measured again. In this case, the results of both measurements may be used, or the average value may be used.

[0058] Furthermore, while the determination of whether a predetermined proportional relationship exists between torque T and damper force FD is based on the magnitude of the deviation between the torque / damper force ratio T / FD and the reference ratio T0 / FD0, it may also be done by directly comparing torque T and damper force FD with their respective reference values. Also, in this embodiment, the difference between the torque / damper force ratio T / FD and the reference ratio T0 / FD0 is used as the deviation, but the ratio of the two may be used instead.

[0059] Furthermore, although a gear motor is used as the hydraulic motor in this embodiment, other types of hydraulic motors, such as piston motors, vane motors, or screw motors, may also be used. Also, although it was explained in this embodiment that ordinary hydraulic oil is used as the damper's hydraulic fluid HF, it goes without saying that other suitable hydraulic oils may be used. In addition, the detailed configuration can be appropriately modified within the scope of the spirit of this invention. [Explanation of Symbols]

[0060] 1. Mass damper (rotational inertia mass damper) 2 liters 2f 1st oil room 2g 2nd oil chamber 3 pistons 4 passages 5. Gear motor (hydraulic motor) 9. Flywheel (rotating mass) 9a Holes in the flywheel (holes formed in the rotating mass) 10 Piston Rods 21 Accumulator 61 Drain hose (drain piping) 63. First hydraulic coupler 64. Second hydraulic coupler 65 Third hydraulic coupler 71. First pressure gauge 72. Second pressure gauge 81 Third pressure gauge HF hydraulic oil T Torque FD damper force Force measured with a spring scale (F) L: Arm length (distance from the center of the rotating mass to the hole) P1 First pressure P2 Second pressure P3 Third pressure Ap Piston Cross-sectional Area T / FD Torque / Damper Force Ratio (Ratio of torque to damper force of detected rotating mass) T0 / FD0 reference ratio

Claims

1. A hydraulic motor type rotational inertia mass damper comprising a cylinder filled with hydraulic fluid, a piston slidably mounted within the cylinder and dividing the inside of the cylinder into a first oil chamber and a second oil chamber, a communication passage bypassing the piston and communicating with the first and second oil chambers, a hydraulic motor positioned in the communication passage, and a rotating mass connected to the hydraulic motor, A damper drive process is performed in which torque is applied to the rotating mass to rotate the rotating mass, and the rotation of the rotating mass is converted into the pressure of the hydraulic fluid by the hydraulic motor to move the piston, A torque detection step for detecting the torque applied to the rotating mass during the damper drive step, A damper force detection step for detecting the damper force generated in the rotational inertia mass damper during the damper driving step, A method for evaluating the integrity of a hydraulic motor-type rotational inertia mass damper, comprising an evaluation step of evaluating the rotational inertia mass damper as being in good condition when a predetermined proportional relationship is established between the torque of the detected rotational mass and the damper force.

2. A method for evaluating the integrity of a hydraulic motor-type rotational inertia mass damper according to claim 1, characterized in that, in the damper driving step, torque is applied to the rotating mass by a spring scale hooked into a hole formed in the rotating mass, and the reaction force from the rotating mass at this time is measured, and in the torque detection step, the torque is detected based on the force measured by the spring scale and the distance from the center of the rotating mass to the hole.

3. A method for evaluating the integrity of a hydraulic motor-type rotational inertia mass damper according to claim 1, characterized in that, in the damper force detection step, the pressures on both sides of the hydraulic motor in the communication passage are measured as first and second pressures, respectively, and the damper force is detected based on the difference between the measured first and second pressures and the cross-sectional area of ​​the piston.

4. A method for evaluating the integrity of a hydraulic motor-type rotational inertia mass damper according to claim 3, characterized in that first and second hydraulic couplers for air bleeding are provided on both sides of the hydraulic motor in the communication passage, and in the damper force detection step, first and second pressure gauges are attached to the first and second hydraulic couplers, respectively, and the first and second pressures are measured using the first and second pressure gauges.

5. A method for evaluating the integrity of a hydraulic motor-type rotational inertia mass damper according to claim 1, characterized in that, in the evaluation step, the ratio of the detected torque of the rotating mass to the damper force is compared with a predetermined reference ratio that should be obtained when the rotational inertia mass damper is in a healthy state, and the rotational inertia mass damper is evaluated as healthy when the degree of deviation between the two is small.

6. The rotational inertia mass damper further comprises a drain pipe connected to the drain passage of the hydraulic motor, an accumulator provided inside the piston rod, which is integrated with the piston, and connected to the drain pipe, which stores a portion of the pressure of the hydraulic motor, and a third hydraulic coupler provided in the drain passage. A method for evaluating the integrity of a hydraulic motor-type rotational inertia mass damper according to any one of claims 1 to 5, further comprising a second evaluation step of attaching a third pressure gauge to the third hydraulic coupler and evaluating the drain pressure of the hydraulic motor and the integrity of the accumulator based on the third pressure measured by the third pressure gauge.

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