JP2013150499A - Vibration control structure of power storage apparatus - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vibration control structure of a power storage apparatus which provides damping to a rotor, thereby suppressing vibrations of the rotor, with a simple structure.SOLUTION: An inner tank 11 housing superconductive magnetic bearings 9, 10 is elastically supported on an outer tank 13 by a vibration damping part 16, and the vibration damping part 16 damps vibrations generated in the inner tank 11. Further, mass on the rotor side is set so as to be heavier than mass on the inner tank 11 side. Thus, a larger amount of energy exciting the rotor is distributed to the relatively lighter fixed body side than the relatively heavier rotor side, and the vibrations are absorbed at the fixed body side where vibration control is easy, not the rotor side where the vibration control is difficult. As a result, contact between superconductive bulk bodies 9a, 10a and superconductive coils 9b, 10b is prevented by suppressing the vibrations of the inner tank 11 at the fixed body side with the vibration damping part 16 and providing damping to the rotor side.

Description

  The present invention relates to a damping structure for a power storage device that suppresses vibrations generated in the rotating body of a power storage device that stores electrical energy as kinetic energy of the rotating body.

  A conventional power storage device includes a rotor that rotates integrally with a flywheel, a bearing device that rotatably supports the rotor, and a low temperature that accommodates the flywheel, rotor, and bearing device under cryogenic and high vacuum conditions. A container (cryostat) or the like is provided (for example, see Patent Document 1). In such a conventional power storage device, the flywheel and the rotor are rotated by surplus power or the like, and the power energy is converted into rotational energy and stored. In this conventional power storage device, it is necessary to suppress the vibration of the rotor and prevent the rotor from contacting the stator. In conventional power storage devices, the rotor is rotated by a mechanical bearing such as a bearing or an active magnetic bearing (AMB) that supports the rotor in a non-contact and rotatable manner by the magnetic attractive force of a normal conductive magnet. Supporting freely is conceivable. However, in the case of a mechanical bearing, the lubricating oil evaporates at a very low temperature / high vacuum, so that it cannot be used. In the case of AMB, in principle, it can be used under cryogenic temperatures / high vacuum, but it is necessary to energize the copper wire coil in AMB. To cool the space, a refrigerator consumes a great deal of electrical energy. For this reason, in the case of AMB, the efficiency of the rotational energy is remarkably reduced, and there is a possibility that the power storage device cannot be established. Furthermore, in the case of AMB, the electromagnetic force generated between the rotor and the stator is proportional to the reciprocal of these gaps, and as this gap increases, the electromagnetic force decreases. It is set as narrow as 1 mm or less. For this reason, in the case of AMB, it is difficult to maintain the assembly accuracy of the power storage device, and even if the assembly accuracy is ensured at room temperature, the heat shrinks uniformly when cooled from room temperature to about -200 to -250 ° C. Otherwise, the rotor and the stator may come into contact with each other due to the difference in distortion due to the material. On the other hand, a magnetic force is applied from the outside of the cryostat to a non-contact magnetic clutch (magnetic force torque transmission component) that transmits torque between the rotating shaft of the motor generator and the rotor in a non-contact manner by magnetic force. It is possible to suppress it. However, in the method of controlling the magnetic force of the non-contact type magnetic clutch, since the controlled object is limited to the end of the rotor, the vibration as a whole cannot be suppressed, and the vibration suppressing effect is limited. is there.

JP 2002-118968 A

  A conventional power storage device generates a magnetic field between a superconducting coil of a superconducting magnetic bearing and a superconducting bulk body, and the superconducting magnetic bearing rotatably supports the rotor in a non-contact manner. In such a conventional power storage device, since the superconducting coil and the superconducting bulk body are used as bearings without contact, there is no or very little damping (damping). For this reason, in the conventional power storage device, when the rotor is vibrated by an external force, there is a problem that the rotor does not attenuate and the rotor contacts the stator.

  The subject of this invention is providing the damping structure of the electric power storage apparatus which can give damping to a rotary body with a simple structure and can suppress the vibration of this rotary body.

The present invention solves the above-mentioned problems by the solving means described below.
In addition, although the code | symbol corresponding to embodiment of this invention is attached | subjected and demonstrated, it is not limited to this embodiment.
As shown in FIG. 1 and FIG. 3, the invention of claim 1 is applied to the rotating body of the power storage device (1) that stores electric energy as kinetic energy of the rotating body (6 b, 7, 8, 9 a, 10 a). A damping structure for a power storage device that suppresses generated vibrations, the rotor (9a, 10a) on the rotating body side and the stator on the stationary body (9b, 10b, 11; 9b, 10b, 11, 13) side A superconducting magnetic bearing (9, 10) that generates a magnetic field between (9b, 10b) and rotatably supports the rotating shaft (7) of the rotating body in a non-contact manner, and vibrations generated in the rotating body A damping structure (15) of a power storage device including a vibration damping section (16; 18) for damping vibration generated in the fixed body that supports the stator.

  The invention according to claim 2 is the vibration damping structure of the power storage device according to claim 1, wherein the mass on the rotating body side is larger than the mass on the stationary body side. .

  According to a third aspect of the present invention, in the vibration damping structure of the power storage device according to the first or second aspect, as shown in FIGS. 1 and 2, the vibration damping portion (16) is formed of the superconducting magnetic bearing. The inner tank (11) that accommodates the superconducting magnetic bearing in a state where the stator is supported is elastically supported by the outer tank (13) that accommodates the inner tank, and vibration generated in the inner tank is attenuated. It is the vibration suppression structure of the electric power storage apparatus characterized.

  According to a fourth aspect of the present invention, in the vibration damping structure for a power storage device according to any one of the first to third aspects, as shown in FIGS. 1 and 2, the damper portion ( 16b) A vibration damping structure for a power storage device, comprising a housing portion (17) for housing the air chamber in the air chamber.

  According to a fifth aspect of the present invention, in the vibration damping structure of the power storage device according to the first or second aspect, as shown in FIG. 3, the superconducting magnetic bearing is supported while the stator of the superconducting magnetic bearing is supported. The inner tank (11) to be accommodated is provided with a support part (19) that supports the outer tank (13) that accommodates the inner tank, and the vibration damping part (18) elastically supports the outer tank, and A vibration damping structure for a power storage device, wherein vibration generated in an inner tank and the outer tank is attenuated.

  According to the present invention, damping can be imparted to the rotating body with a simple structure to suppress vibration of the rotating body.

BRIEF DESCRIPTION OF THE DRAWINGS It is a longitudinal cross-sectional view which shows typically an electric power storage apparatus provided with the damping device of the electric power storage apparatus which concerns on 1st Embodiment of this invention. BRIEF DESCRIPTION OF THE DRAWINGS It is a conceptual diagram which shows typically the structure of the vibration damping part in the damping structure of the power storage device which concerns on 1st Embodiment of this invention, (A)-(D) is a conceptual diagram which shows the dynamic model of a vibration damping part. It is. It is a longitudinal cross-sectional view which shows typically a power storage device provided with the damping device of the power storage device which concerns on 2nd Embodiment of this invention.

(First embodiment)
Hereinafter, a first embodiment of the present invention will be described in detail with reference to the drawings.
A power storage device 1 shown in FIG. 1 is a device that stores electrical energy as kinetic energy of a rotating body. The power storage device 1 converts and stores surplus power into kinetic energy of the flywheel 8 during charging, and converts kinetic energy accumulated in the flywheel 8 into electrical energy during discharge. The power storage device 1 is, for example, a superconducting flywheel power storage device that supports a rotating body by a magnetic support device using a superconductor and stores electric power as kinetic energy of the rotating body. The power storage device 1 includes a motor generator (generator motor) 2, a gantry 3, a joint 4, a connecting shaft 5, a magnetic clutch 6, a rotating shaft 7, a flywheel (flywheel) 8, and a superconducting magnetic bearing. 9, 10, an inner tank 11, a cooling device 12, an outer tank 13, vacuum evacuation devices 14A and 14B, a damping structure 15, and the like.

  The motor generator 2 is a device in which the motor and the generator are reversible and are used together. The motor generator 2 rotates the electric motor with electric energy to rotate the flywheel 8, and generates electric power by rotating the generator with the kinetic energy of the flywheel 8. The motor generator 2 includes a rotating shaft 2a and the like. The gantry 3 is a member that supports the main part of the power storage device 1. The gantry 3 is a frame-like member disposed outside the outer tub 13 and supports the motor generator 2, the compressor 12b, the outer tub 13, the vacuum pumps 14a and 14c, and the like. The joint 4 is a device that connects the rotating shaft 2a on the motor generator 2 side and the connecting shaft 5 on the magnetic clutch 6 side. The joint 4 is, for example, a shaft joint that transmits power between the motor generator 2 and the magnetic clutch 6. The connecting shaft 5 is a member that connects the joint 4 and the magnetic clutch 6. One end of the connecting shaft 5 is fixed to the joint 4 so as to rotate together with the joint 4 and the magnetic clutch 6, and the other end is fixed to the clutch piece 6 a of the magnetic clutch 6. Yes.

  The magnetic clutch 6 is a device that transmits power between the motor generator 2 and the rotary shaft 7. The magnetic clutch 6 is a magnetic force torque transmission component such as a non-contact type magnetic clutch that interrupts power in a non-contact manner. The magnetic clutch 6 includes a clutch piece 6a of a permanent magnet or a coil (for example, copper wire) and a permanent magnet clutch piece 6b that generates a magnetic force between the clutch piece 6a. In the magnetic clutch 6, the clutch piece 6a and the clutch piece 6b are opposed so as to form a gap between the clutch piece 6a and the clutch piece 6b, and the clutch piece 6a is disposed outside the outer tub 13, A clutch piece 6 b is disposed inside the inner tank 11.

  The rotating shaft 7 is a member that rotates integrally with the flywheel 8. The rotary shaft 7 has an upper end fixed to the clutch piece 6 b of the magnetic clutch 6. The flywheel 8 is a member for storing electrical energy as kinetic energy. The flywheel 8 is fixed to the rotary shaft 7 so that the center of the flywheel 8 coincides with the central axis of the rotary shaft 7. The flywheel 8 is housed in a floating state in the inner tank 11 together with the rotating shaft 7 and functions as a superconducting flywheel for storing power.

  The superconducting magnetic bearings 9 and 10 are devices that rotatably support the rotating shaft 7. The superconducting magnetic bearing 9 is disposed above the flywheel 8 and supports the upper end portion side of the rotating shaft 7 in a non-contact manner. The superconducting magnetic bearing 10 is disposed below the flywheel 8 and supports the lower end portion of the rotating shaft 7 in a non-contact manner. The superconducting magnetic bearings 9 and 10 function as thrust bearings that rotatably support the rotating shaft 7 by utilizing magnetic levitation due to the Meissner effect of the superconducting material. The superconducting magnetic bearings 9 and 10 include superconducting bulk bodies (rotors) 9a and 10a, superconducting coils (stators) 9b and 10b, etc., and the superconducting bulk bodies 9a and 10a on the rotating body side and the superconducting coil 9b on the stationary body side. , 10b to generate a magnetic field. Superconducting magnetic bearings 9 and 10 make superconducting bulk bodies 9a and 10a and superconducting coils 9b and 10b and superconducting bulk bodies 9a and 10a and superconducting coils 9b and 10b face each other and generate a magnetic repulsive force therebetween. The rotating shaft 7 is guided so that a predetermined interval is maintained between the two. The superconducting magnetic bearings 9 and 10 support the rotating shaft 7 and the flywheel 8 in a floating state, thereby reducing the frictional resistance of the bearing portion that occupies most of the energy loss.

  The superconducting bulk bodies 9a and 10a are a mass of high-temperature superconducting material having superconducting characteristics equivalent to those of a single crystal. The superconducting bulk bodies 9a and 10a are, for example, melt-growth bodies in which a Y-type superconducting material or the like is dissolved and then grown as crystals, and exhibit superconducting characteristics when cooled. The superconducting bulk bodies 9 a and 10 a are fixed to the outer peripheral surface of the rotating shaft 7 and constitute a part of the rotating body together with the clutch piece 6 b of the magnetic clutch 6, the rotating shaft 7 and the flywheel 8. Superconducting coils 9b and 10b are coils formed by winding a superconducting wire. The superconducting coils 9b and 10b are, for example, ring-shaped members wound with an Nb—Ti-based superconducting material, a bismuth-based high-temperature superconducting material, or a Y-based high-temperature superconducting material, and constitute a part of the fixed body together with the inner tank 11. In addition, the superconducting bulk bodies 9a and 10a are fixed to the inner tank 11 with a space therebetween. In the first embodiment, the mass on the rotating body side constituted by the clutch piece 6b, the rotating shaft 7, the flywheel 8 and the superconducting bulk bodies 9a and 10a is constituted by the superconducting coils 9b and 10b, the inner tank 11 and the refrigerator 12a. It is set to be larger than the mass on the fixed body side.

  The inner tank 11 is a container having a cryogenic temperature / high vacuum inside. The inner tank 11 accommodates the superconducting magnetic bearings 9 and 10 in a state where the superconducting coils 9b and 10b of the superconducting magnetic bearings 9 and 10 are supported. The inner tank 11 is a low-temperature container such as a cryostat that accommodates the clutch piece 6b of the magnetic clutch 6, the rotating shaft 7, the flywheel 8, and the superconducting magnetic bearings 9 and 10 at an extremely low temperature. In the inner tank 11, the portion between the clutch piece 6a and the clutch piece 6b of the magnetic clutch 6 is a non-metallic member such as glass fiber reinforced plastics (GFRP). The inner tank 11 is maintained at an extremely low temperature in order to keep the superconducting coils 9b and 10b of the superconducting magnetic bearings 9 and 10 below the critical temperature, and the inner tank 11 is arranged to reduce the windage loss of the flywheel 8. Maintained under high vacuum.

  The cooling device 12 is a device that cools the inside of the inner tank 11. The cooling device 12 is, for example, a heat conduction type cooling device such as a cryogenic refrigerator that cools the superconducting coils 9b and 10b of the superconducting magnetic bearings 9 and 10 in the inner tank 11 to a critical temperature or lower with liquid nitrogen. The cooling device 12 includes a refrigerator 12a such as a GM (Gifford-McMahon) refrigerator that repeatedly compresses and expands helium gas, a compressor 12b that supplies refrigerant gas to the refrigerator 12a, and a refrigerator The flexible pipe 12c etc. which have the flexibility in which a refrigerant gas flows between 12a and the compressor 12b are provided. In the cooling device 12, the refrigerator 12 a is disposed inside the inner tank 11, and the compressor 12 b is disposed outside the outer tank 13.

  The outer tub 13 is a container whose inside is under a high vacuum. The outer tub 13 is a vacuum heat insulating container that houses the inner tub 11 under high vacuum. The outer tub 13 forms a vacuum heat insulating layer (space) between the inner tub 11 and, unlike the inner tub 11, is not at a very low temperature. The tank 11 is accommodated. In the outer tub 13, as in the inner tub 11, a portion between the clutch piece 6 a and the clutch piece 6 b of the magnetic clutch 6 is a non-metallic member such as GFRP.

  The vacuum exhaust device 14A is a device that puts the inside of the inner tank 11 in a vacuum state, and the vacuum exhaust device 14B is a device that puts the inside of the outer tank 13 in a vacuum state. The vacuum evacuation device 14A has an inside of the inner tank 11 of about several to 100 Pa for heat transfer to the superconducting bulk bodies 9a and 10a (cooling of the superconducting bulk bodies 9a and 10a by cold heat from the superconducting coils 9b and 10b). Adjust to vacuum. The vacuum evacuation device 14A includes a vacuum pump 14a that evacuates the inside of the inner tank 11, a flexible conduit 14b having flexibility that connects the vacuum pump 14a and the inner tank 11, and the like. Similarly, the vacuum evacuation device 14B includes a vacuum pump 14c that evacuates the inside of the outer tank 13, a flexible conduit 14d having flexibility that connects the vacuum pump 14c and the outer tank 13, and the like. .

  The vibration damping structure 15 is a structure that suppresses vibration generated in the rotating body of the power storage device 1. The damping structure 15 is provided on the fixed body side such as the superconducting coils 9b and 10b and the inner tank 11 when the rotating body side such as the clutch piece 6b, the superconducting bulk bodies 9a and 10a, the rotating shaft 7 and the flywheel 8 vibrates due to external force. The vibration on the rotating body side is also attenuated by attenuating the vibration, thereby preventing the superconducting bulk bodies 9a and 10a and the superconducting coils 9b and 10b from colliding with each other. As shown in FIGS. 1 and 2, the vibration damping structure 15 includes a vibration damping portion 16 and a housing portion 17.

  The vibration attenuating unit 16 shown in FIGS. 1 and 2 is a part for attenuating the vibration generated in the fixed body in order to attenuate the vibration generated in the rotating body. The vibration damping unit 16 is a part that elastically supports the inner tank 11 on the outer tank 13 and attenuates vibrations generated in the inner tank 11. The vibration damping unit 16 provides damping to the rotating body side by softly supporting the inner tank 11 from the outer tank 13 without installing a damper under a cryogenic temperature / high vacuum, thereby providing superconducting bulk bodies 9a and 10a and a superconducting coil 9b. , 10b is prevented. The vibration damping portion 16 has one end connected to the outer surface of the inner tub 11 and the other end connected to the inner surface of the outer tub 13, and at least three locations on the upper and lower portions of the inner tub 11. Has been placed. The vibration damping portion 16 includes a spring portion 16a and a damper portion 16b.

  The spring portion 16 a is an elastic body such as a tension coil spring that generates a tensile force that biases the inner tank 11 toward the outer tank 13. The damper portion 16b is a piston-type dashpot (attenuator) that uses a working fluid such as oil or air. The damper portion 16b divides the inside of the cylinder into a head side chamber and a rod side chamber by a piston movably accommodated in the cylinder, and the working fluid in the cylinder is passed through the throttle portion between the head side chamber and the rod side chamber. The vibration is attenuated by the viscous resistance generated when it moves. The vibration damping portion 16 is a Maxwell model in which the spring portion 16a and the damper portion 16b shown in FIG. 2 (A) are arranged in series, and the forked portion in which the spring portion 16a and the damper portion 16b shown in FIG. 2 (B) are arranged in parallel. 2C, a mechanical model such as three elements in which the Maxwell model and the spring portion 16a are arranged in parallel as shown in FIG. 2C, and a four element in which the Maxwell model and the forked model shown in FIG. 2D are arranged in series. It is constituted by.

  The accommodating portion 17 is a portion that accommodates the damper portion 16b of the vibration attenuating portion 16 in the air chamber. The accommodating part 17 is a container which seals the spring part 16a and the damper part 16b, for example. The accommodating portion 17 is previously filled with air so that a damper that can be used at normal room temperature / atmospheric pressure is applicable, and the working fluid evaporates from the damper portion 16b in the outer tank 13 under high vacuum. To prevent it.

Next, the operation of the vibration damping structure for the power storage device according to the first embodiment of the present invention will be described.
When power is stored in the power storage device 1, electrical energy is converted into kinetic energy of the flywheel 8 and stored. The magnetic clutch 6 is energized to generate an electromagnetic force between the clutch piece 6a and the clutch piece 6b, and is connected to the rotary shaft 2a and the rotary shaft 7 of the motor generator 2. Next, the motor generator 2 is caused to function as an electric motor, the motor generator 2 rotates the rotating shaft 7 by surplus electric power, the flywheel 8 rotates together with the rotating shaft 7, and the electric energy is converted into kinetic energy. Accumulated as. At this time, since the magnetic repulsive force acts between the superconducting bulk bodies 9a and 10a of the superconducting magnetic bearings 9 and 10 and the superconducting coils 9b and 10b, the rotating shaft 7 and the flywheel 8 rotate in a floating state. The superconducting magnetic bearings 9 and 10 prevent kinetic energy from being lost due to frictional resistance.

  When taking out electric power from the power storage device 1, the kinetic energy of the flywheel 8 is converted into electric energy and taken out. When the motor generator 2 is caused to function as a generator and the rotating shaft 2a of the motor generator 2 is rotated by the rotational energy of the flywheel 8, the motor generator 2 generates electric power and kinetic energy is extracted as electric energy. . Thus, the surplus power is converted into the kinetic energy of the flywheel 8 and stored in the power storage device 1, and the kinetic energy stored in the flywheel 8 is converted into electrical energy when necessary by the power storage device 1. Electrical energy is extracted.

The magnetic spring formed by the superconducting bulk bodies 9a and 10a and the superconducting coils 9b and 10b causes the superconducting bulk bodies 9a and 10a on the rotating shaft 7 side and the superconducting coils 9b and 10b on the inner tank 11 side to act / react with each other. At this time, since the rotating body and the fixed body are displaced at an inverse ratio of the mass ratio between the rotating body side and the fixed body side, when the mass ratio between the rotating body side and the fixed body side is 1: 1, Relative displacement is minimized. However, in the case of the power storage device 1 using the superconducting magnetic bearings 9 and 10, it is difficult to give damping to the rotating body. In this system, the superconducting bulk bodies 9a and 10a and the superconducting coils 9b and 10b It is difficult to prevent contact. In the first embodiment, for example, the mass on the rotor side is increased so that the mass on the rotor side: the mass on the fixed body side = 10: 1, and the displacement on the fixed body side is 10 times larger than the displacement on the rotor side. In this way, damping is applied by the damper portion 16b of the vibration attenuating portion 16 to suppress vibration of the rotating body. If the ratio of the mass M _R on the rotating body and the mass M _{S on the} stationary body is 1: 1 when energy is input due to disturbance of E [J] as a whole, the energy E _{S on the} stationary body due to the disturbance is 1: 1. In addition, the energy E _R on the rotating body side can be absorbed only by E _S = E _R = E / 2 by the damper. However, this first embodiment, for example, the mass ratio of the rotary body side and the stationary side 10: when set to 1, the action / reaction and the force F _R exerted on the rotary section and a force F _S acting on the fixed body side From the relationship, F _S = −F _R. Therefore, in the first embodiment, the acceleration a _{S on the} fixed body side and the acceleration a _{R on the} rotating body side are | a _S |: | a _R | = F _S / M _S : F _R / M _R = 10: 1 Therefore, since speed v∝acceleration a, E _S : E _R = M _S a _S ² : M _R a _R ² = 10: 1, 10E / 11 can also be absorbed by the damper portion 16b.

The vibration damping structure of the power storage device according to the first embodiment of the present invention has the following effects.
(1) In the first embodiment, a magnetic field is generated between the superconducting bulk bodies 9a, 10a on the rotating body side and the superconducting coils 9b, 10b on the stationary body side, and the rotating shaft 7 of the rotating body is rotated without contact. In order to freely support the superconducting magnetic bearings 9 and 10 and attenuate the vibration generated in the rotating body, the vibration attenuating unit 16 attenuates the vibration generated in the fixed body that supports the superconducting bulk bodies 9a and 10a. For this reason, it is possible to easily suppress the vibration on the rotating body side by attenuating the vibration on the fixed body side rather than the rotating body side on which it is difficult to apply damping by the vibration attenuating unit 16.

(2) In the first embodiment, the mass on the rotating body side is larger than the mass on the stationary body side. For this reason, a large amount of energy for exciting the rotating body is distributed to the stationary body side, which is relatively lighter than the relatively heavy rotating body side, and vibration is generated on the stationary body side where vibration suppression is easy, not on the rotating body side where vibration suppression is difficult. Can be absorbed. As a result, it is possible to prevent contact between the superconducting bulk bodies 9a and 10a and the superconducting coils 9b and 10b by suppressing the vibration on the fixed body side by the vibration attenuating unit 16 and imparting damping to the rotating body side.

(3) In the first embodiment, the vibration attenuating portion 16 is provided in the inner tank 11 that accommodates the superconducting magnetic bearings 9 and 10 while the superconducting bulk bodies 9 a and 10 a are supported, and the outer tank 13 that accommodates the inner tank 11. Is elastically supported, and the vibration attenuator 16 attenuates the vibration generated in the inner tank 11. For this reason, by elastically supporting the inner tank 11 on the fixed body side by the vibration attenuating portion 16, the inner tank 11 on the fixed body side can be vibrated more easily than the rotating body side. As a result, when the rotating shaft 7 on the rotating body side vibrates due to an external force, the vibration of the rotating shaft 7 on the rotating body side can be suppressed by attenuating the vibration of the inner tank 11 on the fixed body side by the vibration damping unit 16. it can.

(4) In the first embodiment, the accommodating portion 17 accommodates the damper portion 16b of the vibration attenuating portion 16 in the air chamber. For this reason, even if the damper part 16b is installed in the outer tank 13 under a high vacuum, the accommodating part 17 can prevent the working fluid from evaporating from the damper part 16b. As a result, an expensive special damper that can be used at an extremely low temperature / high vacuum is not required, and vibration of the rotating shaft 7 can be suppressed by the normal inexpensive damper portion 16b.

(Second Embodiment)
The power storage device 1 shown in FIG. 3 omits the vibration damping unit 16 shown in FIGS. 1 and 2 and includes an elastic support unit 19 and the like. The vibration damping structure 15 shown in FIG. 3 includes the superconducting coils 9b and 10b, the inner tank 11 and the clutch piece 6b, the superconducting bulk bodies 9a and 10a, the rotating shaft 7 and the rotating body 7 such as the flywheel 8 that vibrate due to external force. By attenuating the vibration on the fixed body side such as the outer tub 13, the vibration on the rotating body side is also attenuated to prevent the superconducting bulk bodies 9a and 10a and the superconducting coils 9b and 10b from colliding with each other. The vibration damping structure 15 includes a vibration damping unit 18 and the like.

  The vibration attenuating portion 18 is a portion that elastically supports the outer tub 13 and attenuates vibrations generated in the inner tub 11 and the outer tub 13. The vibration damping unit 18 supports the outer tub 13 from the gantry 3 so as to give damping to the rotating body side and prevent contact between the superconducting bulk bodies 9a and 10a and the superconducting coils 9b and 10b. The vibration attenuating portion 18 includes a spring portion 18a, a damper portion 18b, and the like, similar to the vibration attenuating portion 16 shown in FIG. The spring portion 18 a is an elastic body such as a tension coil spring that generates a tensile force that biases the outer tub 13 toward the gantry 3. The damper portion 18b is a piston-type dashpot (attenuator) using a working fluid such as oil or air, similarly to the damper portion 16b shown in FIG. The vibration attenuating unit 18 is configured by a dynamic model such as a Maxwell model, a forked model, a 3 element, or a 4 element, similarly to the vibration attenuating unit 16 shown in FIG. In the second embodiment, the mass on the rotating body side constituted by the clutch piece 6b, the rotating shaft 7, the flywheel 8 and the superconducting bulk bodies 9a and 10a is determined by the superconducting coils 9b and 10b, the inner tank 11 and the outer tank 13 side. It is set to be heavier than the mass on the fixed body side to be constructed.

  A support portion 19 shown in FIG. 3 is a portion that supports the inner tub 11 in the outer tub 13. The support portion 19 is a member that connects the bottom surface of the inner tub 11 and the upper surface of the outer tub 13 so that the bottom surface of the inner tub 11 is rigidly supported by the upper surface of the outer tub 13, for example. At least three support portions 19 are arranged between the inner tank 11 and the outer tank 13.

The vibration damping structure for a power storage device according to the second embodiment of the present invention has the following effects in addition to the effects of the first embodiment.
(1) In the second embodiment, the inner tank 11 that accommodates the superconducting magnetic bearings 9 and 10 in a state where the superconducting bulk bodies 9a and 10a are supported is replaced by the elastic support portion in the outer tank 13 that accommodates the inner tank 11. 19 is elastically supported, and the vibration damping unit 18 elastically supports the outer tub 13 and attenuates vibrations generated in the inner tub 11 and the outer tub 13. For this reason, when the rotating shaft 7 on the rotating body side is vibrated by an external force, the vibration of the rotating tank 7 on the rotating body side is suppressed by attenuating the vibration of the inner tank 11 and the outer tank 13 on the fixed body side by the vibration attenuating unit 18. be able to. Further, since the vibration damping unit 18 is arranged outside the outer tank 13 without arranging the vibration damping unit 18 in the outer tank 13 under high vacuum, the damper 18b of the vibration damping unit 18 is placed in the air chamber. It is not necessary to accommodate in the accommodating part 17 of the. As a result, a normal air-cooled damper unit 18b can be used for the vibration damping unit 18, and the power storage device 1 can be manufactured at a low cost. Furthermore, since the vibration damping unit 18 is arranged outside the outer tub 13, the load on the cooling device 12 is not increased at all, and the efficiency of rotational energy can be prevented from decreasing.

(2) In the second embodiment, the mass on the rotating body side is heavier than the mass on the stationary body side. For this reason, the vibration of the inner tank 11 and the outer tank 13 on the fixed body side is suppressed by the vibration attenuating portion 18 and damping is applied to the rotating body side to prevent contact between the superconducting bulk bodies 9a and 10a and the superconducting coils 9b and 10b. can do.

(Other embodiments)
The present invention is not limited to the embodiment described above, and various modifications or changes can be made as described below, and these are also within the scope of the present invention.
(1) In this embodiment, the magnetic clutch 6 in which the clutch piece 6a is a permanent magnet or coil and the clutch piece 6b is a permanent magnet has been described as an example. However, the present invention also applies to a magnetic clutch using a superconducting bulk body. Can be applied. Further, in this embodiment, the case where the ratio of the mass on the solid body side and the mass on the rotating body side is 1:10 has been described as an example, but the mass ratio is not limited to 1:10, An arbitrary mass ratio can be set so that the mass on the solid body side is larger than the mass on the rotating body side. Further, in this embodiment, the case where the flywheel 8 is accommodated in the inner tank 11 together with the superconducting magnetic bearings 9 and 10 has been described as an example. However, only the superconducting magnetic bearings 9 and 10 may be accommodated in the inner tank 11. it can.

(2) In this embodiment, the case where a part of the outer tub 13 between the clutch piece 6a and the clutch piece 6b of the magnetic clutch 6 is constituted by a non-metallic member has been described as an example. The tank 12 can be omitted and the non-metallic member of the inner tank 11 can be exposed to the atmosphere. In this embodiment, the case where the refrigerator 12a of the cooling device 12 is a GM refrigerator has been described as an example. However, the present invention can also be applied to a case of another type of refrigerator. Furthermore, in this embodiment, the case where the inner tank 11 and the outer tank 13 are brought into a vacuum state by the vacuum exhaust devices 14A and 14B has been described as an example. However, after the vacuum degree inside these reaches a predetermined value, It can also be sealed to prevent leakage.

(3) In this embodiment, the case where the vibration damping parts 16 and 18 are configured by the spring parts 16a and 18a and the damper parts 16b and 18b has been described as an example. The vibration attenuating portions 16 and 18 can be configured by the 18a and the damper portions 16b and 18b. Further, in this embodiment, the case where the vibration damping units 16 and 18 are disposed above and below the inner tank 11 and the outer tank 13 has been described as an example. However, vibration is generated below or above the inner tank and the outer tank 13. Attenuating parts 16 and 18 can also be arranged. Furthermore, in the first embodiment, the case where the spring portion 16a and the damper portion 16b of the vibration damping portion 16 are accommodated in the accommodating portion 17 has been described as an example. However, only the damper portion 16b is accommodated in the accommodating portion 17. You can also

DESCRIPTION OF SYMBOLS 1 Power storage device 2 Motor generator 3 Base 4 Joint 5 Connection shaft 6 Magnetic clutch 7 Rotating shaft 8 Flywheel 9,10 Superconducting magnetic bearing 9a, 10a Superconducting bulk body (rotor)
9b, 10b Superconducting coil (stator)
DESCRIPTION OF SYMBOLS 11 Inner tank 12 Cooling device 13 Outer tank 14A, 14B Vacuum exhaust apparatus 15 Damping structure 16 Vibration damping part 16a Spring part 16b Damper part 17 Housing part 18 Vibration damping part 18a Spring part 18b Damper part 19 Support part

Claims (5)

A power storage device damping structure for suppressing vibration generated in the rotating body of the power storage device that stores electrical energy as kinetic energy of the rotating body,
A superconducting magnetic bearing that generates a magnetic field between the rotor on the rotating body side and the stator on the stationary body side, and rotatably supports the rotating shaft of the rotating body in a non-contact manner;
A vibration attenuator for attenuating vibration generated in the fixed body that supports the stator in order to attenuate vibration generated in the rotating body;
A damping structure for a power storage device comprising: In the vibration damping structure of the power storage device according to claim 1,
The mass on the rotating body side is larger than the mass on the stationary body side,
The vibration control structure of the power storage device characterized by the above. In the vibration damping structure of the power storage device according to claim 1 or 2,
The vibration damping unit elastically supports an inner tank that accommodates the superconducting magnetic bearing in a state in which the stator of the superconducting magnetic bearing is supported, and an vibration generated in the inner tank. Attenuating,
The vibration control structure of the power storage device characterized by the above. In the damping structure of the power storage device according to any one of claims 1 to 3,
A housing portion for housing the damper portion of the vibration damping portion in an air chamber;
The vibration control structure of the power storage device characterized by the above. In the vibration damping structure of the power storage device according to claim 1 or 2,
A support portion for supporting the inner tank containing the superconducting magnetic bearing in a state where the stator of the superconducting magnetic bearing is supported, and supporting the outer tank containing the inner tank;
The vibration damping unit elastically supports the outer tub and attenuates vibration generated in the inner tub and the outer tub.
The vibration control structure of the power storage device characterized by the above.

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