Large variable moment of inertia flywheel

Abstract

The application provides a large variable moment of inertia flywheel, which comprises a flywheel body, a mass center adjusting mechanism and a hydraulic transmission system, mass center adjusting mechanisms are arranged on two end faces of the flywheel body, and a plurality of mass center adjusting mechanisms are uniformly arranged on the end faces of the flywheel body at equal distances with the axis of the flywheel body as the center, and the hydraulic transmission system is arranged in a through groove between the two end faces of the flywheel body and is used for driving the mass center adjusting mechanisms to adjust the moment of inertia of the flywheel. The application can actively change the moment of inertia of the flywheel within a certain range, can conveniently realize active release or absorption of mechanical energy of the flywheel, and improves the flexibility of the flywheel energy storage device.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of flywheel energy storage devices, in particular to a large variable moment of inertia flywheel. BACKGROUND

[0002] Flywheel energy storage technology has a long history, and is widely used in aerospace, power, automobile and other industries today, and has the advantages of long service life, fast energy storage and release speed, high efficiency and the like, so that the technology has been closely watched. However, the moment of inertia of the existing large flywheel is determined after being manufactured and cannot be changed, and the structure is simple but the flexibility is low. SUMMARY

[0003] The present application aims at the deficiencies of the prior art, and provides a large variable moment of inertia flywheel.

[0004] The specific technical solutions are as follows:

[0005] A large variable moment of inertia flywheel, comprising a flywheel body, a mass center adjusting mechanism and a hydraulic transmission system, the mass center adjusting mechanism is arranged on both end faces of the flywheel body, and a plurality of mass center adjusting mechanisms are uniformly arranged on the end faces of the flywheel body at equal distances with the axis of the flywheel body as the center, and the hydraulic transmission system is arranged in the through groove between the two end faces of the flywheel body to drive the mass center adjusting mechanism to adjust the moment of inertia of the flywheel.

[0006] Optionally, the mass center adjusting mechanism comprises a mass block, a lead screw, a lead screw top plug and a tapered roller bearing, the mass block is in sliding contact with the inner side end face of the flywheel body along the radial direction of the flywheel body, the length direction of the lead screw is consistent with the radial direction of the flywheel body, the lead screw penetrates the mass block and is threadedly connected with the mass block, the lead screw top plug is fixed on the outer ring of the flywheel body, one end of the lead screw is rotationally connected to the lead screw top plug, and the other end of the lead screw is fixedly connected with the execution end of the hydraulic transmission system.

[0007] Optionally, the hydraulic transmission system comprises a hydraulic motor, an oil supply part and a shunt part, the oil supply part is used for supplying hydraulic oil to the hydraulic motor, and the shunt part is used for guiding the oil circuit.

[0008] Optionally, the oil supply part comprises an oil supply component and a compensation component, the oil supply component comprises a brushless DC motor, a shaft coupling and a bidirectional plunger pump, a pump shaft of the bidirectional plunger pump is fixedly connected with an output shaft of the brushless DC motor through the shaft coupling, a first port of the bidirectional plunger pump is connected in communication with a first oil port of the hydraulic motor through a first pipeline, a second port of the bidirectional plunger pump is connected in communication with a second oil port of the hydraulic motor through a second pipeline, and the compensation component is used for compensating oil line leakage.

[0009] Optionally, the flow dividing component comprises a first one-way flow dividing valve, a first one-way valve group, a second one-way flow dividing valve and a second one-way valve group, the first one-way flow dividing valve is arranged on the first pipeline and is used for guiding hydraulic oil to flow in a direction consistent with the bidirectional plunger pump to the hydraulic motor, the first one-way valve group is connected in parallel with the first one-way flow dividing valve, and the first one-way valve group is used for guiding hydraulic oil to flow in a direction consistent with the hydraulic motor to the bidirectional plunger pump, the second one-way flow dividing valve is arranged on the second pipeline and is used for guiding hydraulic oil to flow in a direction consistent with the bidirectional plunger pump to the hydraulic motor, the second one-way valve group is connected in parallel with the second one-way flow dividing valve, and the second one-way valve group is used for guiding hydraulic oil to flow in a direction consistent with the hydraulic motor to the bidirectional plunger pump.

[0010] Optionally, the compensation component further comprises an accumulator, a first safety valve, a second safety valve and a third one-way valve, the accumulator is connected in one-way communication with a leakage port of the bidirectional plunger pump, an inlet of the first safety valve is connected with the first pipeline, an outlet of the first safety valve is connected with a pipeline of the accumulator, an inlet of the second safety valve is connected with the second pipeline, an outlet of the second safety valve is connected in communication with the pipeline of the accumulator, and the third one-way valve is used for guiding hydraulic oil leaked from the bidirectional plunger pump to flow to the accumulator.

[0011] Optionally, the compensation component further comprises a fourth one-way valve and a fifth one-way valve, an inlet of the fourth one-way valve is connected in communication with the accumulator, an outlet of the fourth one-way valve is connected in communication with the first pipeline, an inlet of the fifth one-way valve is connected in communication with the accumulator, and an outlet of the fourth one-way valve is connected in communication with the second pipeline.

[0012] Optionally, the accumulator is connected with the first pipeline through a two-position three-way directional valve, when the two-position three-way directional valve is in a first working state, the first pipeline is connected in communication with the first oil port of the hydraulic motor, and when the two-position three-way directional valve is in a second working state, the first pipeline is connected in communication with the accumulator.

[0013] Compared with the prior art, the present application has the following beneficial effects:

[0014] 1. The application drives the hydraulic motor to rotate through the hydraulic oil source, the hydraulic motor drives the screw rod to rotate and further drives the mass block to axially displace, when the mass block centroid position is displaced radially relative to the flywheel rotation center, the flywheel moment of inertia will be actively changed, according to the angular momentum conservation, if the flywheel moment of inertia is actively reduced / raised under the condition that the flywheel has no external torque, the flywheel angular velocity will be actively increased / decreased, and the active release and absorption of the mechanical energy stored in the flywheel are realized;

[0015] 2. The hydraulic transmission system provided by the application provides reliable power support for the large variable moment of inertia flywheel, the hydraulic transmission system is a one-to-three pump controlled motor system, a bidirectional plunger pump is driven by a brushless DC motor, the oil output by the plunger pump is equally divided into three parts by a shunt valve, and the three hydraulic motors are provided with the three parts respectively; in order to compensate the uneven distribution of the mass block caused by the cumulative error of the shunt valve, a group of two-position three-way reversing valves are connected in series before the hydraulic motor, and are used for adjusting the distribution of a certain mass block or two mass blocks; the shunt valve has one on each side of the plunger pump and is respectively connected in parallel with a group of check valves, so as to ensure the normal backflow of the oil. BRIEF DESCRIPTION OF DRAWINGS

[0016] Figure 1 The overall structure schematic diagram of the large variable moment of inertia flywheel provided by the embodiment of the application is shown;

[0017] Figure 2 The explosion mechanism schematic diagram for showing the centroid adjustment mechanism in the large variable moment of inertia flywheel provided by the embodiment of the application is shown;

[0018] Figure 3 The front view structure schematic diagram of the large variable moment of inertia flywheel provided by the embodiment of the application is shown;

[0019] Figure 4 The cross-sectional structure schematic diagram for showing the internal position relationship between the centroid adjustment mechanism and the hydraulic assembly in the large variable moment of inertia flywheel provided by the embodiment of the application is shown;

[0020] Figure 5 The principle diagram of the hydraulic transmission system in the large variable moment of inertia flywheel provided by the embodiment of the application is shown.

[0021] In the figure: 1, flywheel main body; 2, mass center adjusting mechanism; 21, mass block; 22, screw rod; 23, screw rod top plug; 24, tapered roller bearing; 3, hydraulic transmission system; 31, hydraulic motor; 301, first oil port; 302, second oil port; 32, oil supply part; 321, brushless DC motor; 322, shaft coupling; 323, bidirectional plunger pump; 3231, first port; 3232, second port; 324, first pipeline; 325, second pipeline; 326, accumulator; 3261, fourth one-way valve; 3262, fifth one-way valve; 3263, two-position three-way directional control valve; 327, first safety valve; 328, second safety valve; 329, third one-way valve; 33, shunt part; 331, first one-way shunt valve; 332, first one-way valve group; 333, second one-way shunt valve; 334, second one-way valve group. DETAILED DESCRIPTION

[0022] The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative work fall within the scope of protection of the present application.

[0023] It should be noted that the embodiments in the present application and the features in the embodiments can be combined with each other without conflict.

[0024] The present application will be further described below with reference to the drawings and specific embodiments, but not as a limitation of the present application.

[0025] The large variable moment of inertia flywheel provided in the present application refers to Figures 1-4 , including a flywheel main body 1, a mass center adjusting mechanism 2 and a hydraulic transmission system 3, the mass center adjusting mechanism 2 is arranged on both end faces of the flywheel main body 1, and a plurality of mass center adjusting mechanisms 2 are evenly distributed on the end faces of the flywheel main body 1 at equal distances with the axis of the flywheel main body 1 as the center. In this embodiment, three groups of mass center adjusting mechanisms 2 are arranged on each end face of the flywheel, and the mass center adjusting mechanisms 2 at both ends of the flywheel are staggered arranged at a space angle of 60°. The hydraulic transmission system 3 is arranged in the through groove between the two end faces of the flywheel main body 1 to drive the mass center adjusting mechanism 2 to adjust the moment of inertia of the flywheel.

[0026] The center of mass adjusting mechanism 2 comprises a mass block 21, a screw rod 22, a screw rod top plug 23 and a tapered roller bearing 24, a plurality of mass blocks 21 are uniformly distributed on the flywheel body 1 with the center of the flywheel body 1 as the center, and the plurality of mass blocks 21 are slidingly connected to the end face of the flywheel body 1 along the radial direction of the flywheel body 1, the length direction of the screw rod 22 is arranged to be consistent with the radial direction of the flywheel body 1, the screw rod 22 is threadedly connected to the mass block 21, the screw rod top plug is connected to the threaded hole at the outer edge of the flywheel body 1 through a common thread, the center of mass position of the mass block 21 can be finely adjusted, the static balance of the flywheel body 1 in the initial state is ensured, and the tapered roller bearing 24 is arranged between the outer ring of the flywheel body 1 and the end of the screw rod 22 close to the outer ring, and the screw rod 22 is rotatably connected to the screw rod top plug 22.

[0027] The screw rod 22 is driven to rotate forward and reversely, the screw rod 22 can drive the mass block 21 to slide on the end face of the flywheel body 1 along the radial direction of the flywheel body 1 to approach or move away from the axis center of the flywheel body 1, the distance between the mass block 21 and the axis center of the flywheel body 1 is changed, the flywheel rotational inertia is actively changed, according to the angular momentum conservation, if the flywheel rotational inertia is actively reduced under the condition that no external torque is applied to the flywheel, the flywheel angular velocity will actively increase, the active release of the mechanical energy stored in the flywheel is realized, and the flexibility of the flywheel energy storage device can be improved.

[0028] With reference to Figure 5 , the hydraulic transmission system 3 comprises a hydraulic motor 31, an oil supply part 32 and a flow dividing part 33, one hydraulic motor 31 is arranged corresponding to each group of center of mass adjusting mechanisms 2, the output shaft of the hydraulic motor 31 is fixedly connected to the end of the screw rod 22, and the hydraulic transmission system 3 is provided in two groups, the three groups of center of mass adjusting mechanisms 2 on one end face correspond to one group of hydraulic transmission systems 3, the hydraulic transmission system 3 is arranged in the through groove of the flywheel body 1, and the distribution of the elements in the through groove is staggered and symmetrically arranged at a space angle of 180°, the oil supply part 32 is used for supplying hydraulic oil to the hydraulic motor 31, and the flow dividing part 33 is used for guiding the oil path.

[0029] Specifically, in order to effectively ensure the stability of the hydraulic transmission system 3, the oil supply part 32 comprises an oil supply assembly and a compensation assembly, the oil supply assembly comprises a brushless DC motor 321, a shaft coupling 322 and a bidirectional plunger pump 323, the pump shaft of the bidirectional plunger pump 323 is fixedly connected to the output shaft of the brushless DC motor 321 through the shaft coupling 322, the first port 3231 of the bidirectional plunger pump 323 is in communication with the first oil port 301 of the hydraulic motor 31 through a first pipeline 324, the second port 3232 of the bidirectional plunger pump 323 is in communication with the second oil port 302 of the hydraulic motor 31 through a second pipeline 325, and the compensation assembly is used for compensating the oil path leakage.

[0030] The shunt part 33 comprises a first one-way shunt valve 331, a first one-way valve group 332, a second one-way shunt valve 333 and a second one-way valve group 334, three flow channels are arranged in the first one-way shunt valve 331 and the second one-way shunt valve 333, the first one-way valve group 332 and the second one-way valve group 334 each comprises three one-way valves, each hydraulic motor 31 is connected with a corresponding flow channel, the first one-way shunt valve 331 is arranged on the first pipeline 324 and is used for guiding the hydraulic oil to flow in the same direction as the bidirectional plunger pump 323 to the hydraulic motor 31, the inlet of the first one-way shunt valve 331 is connected with the first port 3231 of the bidirectional plunger pump 323, the outlet of the first one-way shunt valve 331 is connected with the first oil port 301 of the hydraulic motor 31, the first one-way valve group 332 is connected with the first one-way shunt valve 331 in parallel, and the first one-way valve group 332 is used for guiding the hydraulic oil to flow in the same direction as the hydraulic motor 31 to the bidirectional plunger pump 323, the inlet of the first one-way valve group 332 is connected with the pipeline at the outlet of the first one-way valve group 332, and the outlet of the first one-way valve group 332 is connected with the pipeline at the inlet of the first one-way shunt valve 331.

[0031] The second one-way shunt valve 333 is arranged on the second pipeline 325 and is used for guiding the hydraulic oil to flow in the same direction as the bidirectional plunger pump 323 to the hydraulic motor 31, the inlet of the second one-way shunt valve 333 is connected with the second port 3232 of the bidirectional plunger pump 323, the outlet of the second one-way shunt valve 333 is connected with the second oil port 302 of the hydraulic motor 31, the second one-way valve group 334 is connected with the second one-way shunt valve 333 in parallel and is used for guiding the hydraulic oil to flow in the same direction as the hydraulic motor 31 to the bidirectional plunger pump 323, the inlet of the second one-way valve group 334 is connected with the pipeline at the outlet of the second one-way valve group 334, and the outlet of the second one-way valve group 334 is connected with the pipeline at the inlet of the second one-way shunt valve 333.

[0032] When the brushless direct current motor 321 drives the bidirectional plunger pump 323 to rotate clockwise, the hydraulic oil from the first port 3231 of the bidirectional plunger pump 323 passes through the first one-way shunt valve 331 and enters the hydraulic motor 31 through the first oil port 301 of the hydraulic motor 31, and the hydraulic oil from the second oil port 302 of the hydraulic motor 31 enters the bidirectional plunger pump 323 through the second port 3232 of the bidirectional plunger pump 323 through the second one-way valve group 334; when the brushless direct current motor 321 drives the bidirectional plunger pump 323 to rotate counterclockwise, the hydraulic oil from the second port 3232 of the bidirectional plunger pump 323 passes through the second one-way shunt valve 333 and enters the hydraulic motor 31 through the second oil port 302 of the hydraulic motor 31, and the hydraulic oil from the second oil port 302 of the hydraulic motor 31 enters the bidirectional plunger pump 323 through the first port 3231 of the bidirectional plunger pump 323 through the first one-way valve group 332.

[0033] The compensation component comprises an accumulator 326, a first safety valve 327, a second safety valve 328 and a third check valve 329. The accumulator 326 is connected to the bidirectional plunger pump 323. The inlet of the first safety valve 327 is connected to the first pipeline 324. The outlet of the first safety valve 327 is connected to the accumulator 326. The inlet of the second safety valve 328 is connected to the second pipeline 325. Another outlet of the first safety valve 327 is connected to the accumulator 326. The third check valve 329 is arranged on a pipeline between the accumulator 326 and the bidirectional plunger pump 323, and is used to guide the hydraulic oil to flow from the bidirectional plunger pump 323 to the accumulator 326. The inlet of the third check valve 329 is connected to the bidirectional plunger pump 323. The outlet of the third check valve 329 is connected to the accumulator 326.

[0034] In addition, the compensation component further comprises a fourth check valve 3261 and a fifth check valve 3262. The inlet of the fourth check valve 3261 is connected to the accumulator 326. The outlet of the fourth check valve 3261 is connected to the first pipeline 324. The inlet of the fifth check valve 3262 is connected to the accumulator 326. The outlet of the fourth check valve 3261 is connected to the second pipeline 325.

[0035] The first safety valve 327 and the second safety valve 328 are in a normally closed state under the action of spring force. When the system pressure exceeds a specified value, the first safety valve 327 or the second safety valve 328 is opened to discharge the hydraulic oil in the system into the accumulator 326, so as to effectively ensure that the system pressure does not exceed the allowable value, thereby ensuring that the system does not have an accident due to excessively high pressure. The accumulator 326 is used to store the oil required by the closed hydraulic circuit and the oil required to be supplemented due to the leakage of the hydraulic oil, and is also used to maintain the oil suction pressure of the bidirectional pump and supplement the oil to the low-pressure oil suction side. The third check valve 329 guides the hydraulic oil leaked from the bidirectional plunger pump 323 to the accumulator 326. The accumulator 326 can supplement the oil to the low-pressure side of the bidirectional plunger pump 323 through the fourth check valve 3261 or the fifth check valve 3262.

[0036] The accumulator 326 is connected with the first pipeline 324 through a two-position three-way directional valve 3263, the two-position three-way directional valve 3263 is installed on the left side loop of the double-acting plunger pump 323 (i.e. the hydraulic motor 31 drives the mass block 21 to the outside direction of the flywheel), facilitating technicians to adjust, and each hydraulic motor 31 corresponds to a two-position three-way directional valve 3263, the two-position three-way directional valve 3263 is in the first working state (normal working state), at this time, the first pipeline 324 is in communication with the first oil port 301 of the hydraulic motor 31; if the mass block 21 is found to be unevenly distributed on the end face of the flywheel body 1, causing the overall force to be unbalanced, the two-position three-way directional valve 3263 corresponding to the mass block 21 is adjusted to the second working state (adjustment state), so that the corresponding pipeline is in communication with the accumulator 326, and then the corresponding hydraulic motor 31 drives the mass block 21 to adjust the position, therefore, the two-position three-way directional valve 3263 can adjust the distribution state when the mass block 21 is unevenly distributed along the circumferential direction of the flywheel body 1.

[0037] The above merely describes the preferred embodiments of the present application, and is not intended to limit the implementation and protection scope of the present application. Those skilled in the art should be able to realize that any equivalent replacement and obvious changes made according to the content of the present application should be included in the protection scope of the present application.

Claims

1. A large variable moment of inertia flywheel, characterized by, The application relates to a flywheel body, a mass center adjusting mechanism and a hydraulic transmission system, mass center adjusting mechanisms are arranged on two end faces of the flywheel body, a plurality of the mass center adjusting mechanisms are uniformly arranged on the end faces of the flywheel body at equal distances and with the axis of the flywheel body as the center, the hydraulic transmission system is arranged in a through groove between the two end faces of the flywheel body and is used for driving the mass center adjusting mechanism to adjust the rotational inertia of the flywheel; the mass center adjusting mechanism comprises a mass block, a screw rod, a screw rod top plug and a tapered roller bearing, the mass block is in sliding contact with the inner end face of the flywheel body along the radial direction of the flywheel body, the length direction of the screw rod is consistent with the radial direction of the flywheel body, the screw rod penetrates through the mass block and is threadedly connected with the mass block, the screw rod top plug is fixed on the outer ring of the flywheel body, one end of the screw rod is rotationally connected to the screw rod top plug, and the other end of the screw rod is fixedly connected with the executing end of the hydraulic transmission system; the hydraulic transmission system comprises a hydraulic motor, an oil supply part and a shunt part, the oil supply part is used for supplying the hydraulic motor with hydraulic oil, and the shunt part is used for guiding the oil passage; the oil supply part comprises an oil supply component and a compensation component, the oil supply component comprises a brushless direct-current motor, a shaft coupling and a bidirectional plunger pump, the pump shaft of the bidirectional plunger pump is fixedly connected with the output shaft of the brushless direct-current motor through the shaft coupling, the first port of the bidirectional plunger pump is connected with the first oil port of the hydraulic motor through a first pipeline, the second port of the bidirectional plunger pump is connected with the second oil port of the hydraulic motor through a second pipeline, and the compensation component is used for compensating oil passage leakage; the shunt part comprises a first one-way shunt valve, a first one-way valve group, a second one-way shunt valve and a second one-way valve group, the first one-way shunt valve is arranged on the first pipeline and is used for guiding the hydraulic oil to flow in the same direction as the bidirectional plunger pump to the hydraulic motor, the first one-way valve group is connected with the first one-way shunt valve in parallel, and the first one-way valve group is used for guiding the hydraulic oil to flow in the same direction as the hydraulic motor to the bidirectional plunger pump, the second one-way shunt valve is arranged on the second pipeline and is used for guiding the hydraulic oil to flow in the same direction as the bidirectional plunger pump to the hydraulic motor, the second one-way valve group is connected with the second one-way shunt valve in parallel, and the second one-way valve group is used for guiding the hydraulic oil to flow in the same direction as the hydraulic motor to the bidirectional plunger pump; the compensation component further comprises an accumulator, a first safety valve, a second safety valve and a third one-way valve, the accumulator is connected with the oil leakage port of the bidirectional plunger pump in a one-way manner, the inlet of the first safety valve is connected with the first pipeline, the outlet of the first safety valve is connected with the pipeline of the accumulator, the inlet of the second safety valve is connected with the second pipeline, the outlet of the second safety valve is connected with the pipeline of the accumulator, and the third one-way valve is used for guiding the hydraulic oil leaked from the bidirectional plunger pump to flow to the accumulator.The compensation component further comprises a fourth one-way valve and a fifth one-way valve, an inlet of the fourth one-way valve being communicated with the accumulator, an outlet of the fourth one-way valve being communicated with the first pipeline, an inlet of the fifth one-way valve being communicated with the accumulator, an outlet of the fourth one-way valve being communicated with the second pipeline; the accumulator is connected with the first pipeline through a two-position three-way directional valve, when the two-position three-way directional valve is in a first working state, the first pipeline is communicated with a first oil port of the hydraulic motor, when the two-position three-way directional valve is in a second working state, the first pipeline is communicated with the accumulator.

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