CN117759512A - Energy-storage ocean temperature difference energy underwater conversion device - Google Patents
Energy-storage ocean temperature difference energy underwater conversion device Download PDFInfo
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- CN117759512A CN117759512A CN202311765004.4A CN202311765004A CN117759512A CN 117759512 A CN117759512 A CN 117759512A CN 202311765004 A CN202311765004 A CN 202311765004A CN 117759512 A CN117759512 A CN 117759512A
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
- Y02E10/30—Energy from the sea, e.g. using wave energy or salinity gradient
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Abstract
The invention discloses an energy-storage type ocean temperature difference energy underwater conversion device, which comprises: a heat source pump for providing ocean surface temperature seawater; the cold energy transport bin is used for providing deep ocean cold sea water; the cold energy transportation bin comprises a gas-liquid phase change cavity, an oil storage cavity and an elastic oil bag, and the oil storage cavity is communicated with the elastic oil bag; the gas-liquid phase change cavity comprises a phase change material cavity and a first balance cavity, and the oil storage cavity comprises an oil cavity and a second balance cavity; when the volume of the oil cavity is increased, the elastic oil bag is contracted, and the buoyancy of the cold energy transportation bin is reduced; when the volume of the oil cavity is reduced, the elastic oil bag is increased, and the buoyancy of the cold energy transportation bin is increased; the power generation bin is anchored on the seabed and provides a running track for the cold energy transport bin. The invention provides an energy storage type ocean temperature difference energy underwater conversion device, which is a novel solution to the problem of energy supply of an underwater autonomous vehicle working in a long self-sustaining large sea area.
Description
Technical Field
The invention relates to the technical field of autonomous underwater vehicle energy supply, in particular to an energy storage type ocean temperature difference energy underwater conversion device.
Background
The autonomous underwater vehicle is a device capable of monitoring and detecting underwater states, is ocean high-tech equipment for the development of the strong ocean, is a development focus of the strong ocean in China, and is widely applied to the fields of ocean environment investigation, submarine resource investigation and the like. At present, the energy required by autonomous underwater vehicles mainly depends on a self-carried storage battery pack, and the problem of short task time sequence (less than 1 week), narrow working sea area (hundred kilometers), shallow working depth (kilometers) and high loss rate (more than 40%) is caused by a limited power source. It is critical to solve the above problems to find a safe and reliable continuous energy replenishment solution.
As the only renewable ocean energy source which can be captured and converted in place in the deep sea by the autonomous underwater vehicle, the ocean temperature difference energy power generation technology is the most feasible scheme for solving the problem of long-term energy supply of the autonomous underwater vehicle. The existing ocean temperature difference energy driven aircraft power system converts heat energy into hydraulic oil pressure energy through the melting and expanding process of solid-liquid phase change materials in a warm sea water area, capture of ocean temperature difference energy is achieved, the heat energy-pressure energy conversion efficiency of the solid-liquid phase change process is only 0.7%, and the thermoelectric conversion efficiency of the technology is greatly limited. The thermal cycle power generation transmits the temperature difference energy to the cycle working medium through the heat exchanger to capture the ocean temperature difference energy, and the theoretical efficiency of the process is 100%, so that the technology has higher thermoelectric conversion efficiency. However, the ocean temperature difference energy is mainly used for establishing a large megawatt power generation platform at present, and the application of the existing ocean temperature difference energy thermodynamic cycle power generation platform in an autonomous underwater vehicle is limited by the cold sea water transportation mode of a cold sea water pipeline, and the consumption of the cold sea water pump causes excessive system consumption, so that the net output power of the temperature difference energy power generation system is reduced. The power consumption in the deep sea water cooling energy transportation process is eliminated or reduced, and the method has remarkable benefit for improving the net power generation of the ocean temperature difference energy power generation device. The intermittent autonomous rising submerged cold energy transportation is used as a preferable scheme of cold energy supply, is influenced by ocean tide and submerged depth in practical application, and is not easy to solve the problems of inconvenient communication and inaccurate positioning. In addition, how to realize autonomous butt joint and cold energy transfer between cold energy transport equipment and cold energy required components in the power generation thermodynamic cycle is not good. Therefore, the method for fixing the motion trail of the autonomous lifting and diving equipment, constructing the communication method between the autonomous lifting and diving equipment and the power generation bin conveniently and quickly, designing a low-energy-consumption and high-benefit cold energy transmission mode and bringing the intermittent autonomous lifting and diving cold energy transportation scheme into practical application has important significance. Finally, the energy storage and transportation process of a single cold energy transportation device often consumes a great deal of time, so that the intermittence of the ocean temperature difference energy power generation process adopting the power-free cold source transportation mode is strong, and the time efficiency of power generation is low. Therefore, the time interval between the front and back power generation processes is shortened, and the output electric quantity of the power generation system in unit time can be greatly improved.
Disclosure of Invention
The invention aims to solve the technical problem of providing an energy storage type ocean temperature difference energy underwater conversion device taking an unpowered ascending submerged cold energy transportation bin as a core.
In order to solve the technical problems, the invention provides the following technical scheme:
an energy-storage ocean temperature difference energy underwater conversion device, comprising:
a heat source pump for providing ocean surface temperature seawater;
the cold energy transport bin is used for providing deep ocean cold sea water; the cold energy transportation bin comprises a gas-liquid phase change cavity, an oil storage cavity and an elastic oil bag, and the oil storage cavity is communicated with the elastic oil bag; the gas-liquid phase change cavity comprises a phase change material cavity and a first balance cavity, and the oil storage cavity comprises an oil cavity and a second balance cavity; a linkage mechanism is arranged between the gas-liquid phase-change cavity and the oil storage cavity, and the linkage mechanism synchronously increases or reduces the volume of the oil cavity when the volume of the phase-change material in the phase-change material cavity is increased or reduced due to the volume change in the evaporation-condensation process of the phase-change material; when the volume of the oil cavity is increased, the elastic oil bag is contracted, and the buoyancy of the cold energy transportation bin is reduced; when the volume of the oil cavity is reduced, the elastic oil bag is increased, and the buoyancy of the cold energy transportation bin is increased;
the power generation bin is used for generating power and storing by utilizing the temperature difference between the ocean surface layer temperature seawater provided by the heat source pump and the ocean deep cold seawater provided by the cold energy transportation bin;
and
And the multifunctional anchoring structure anchors the power generation bin on the seabed and provides a running track for the cold energy transportation bin.
The energy-storage type ocean temperature difference energy underwater conversion device takes the temperature difference between ocean surface seawater and deep seawater as a driving force, and the ocean temperature difference energy is less influenced by climate and environment, so the device can realize continuous electric quantity output. The cold energy transportation bin transports cold energy through the periodic condensation-evaporation process of the gas-liquid phase change material between the seabed and the sea surface, and the unpowered ascending and descending of the cold energy transportation bin are realized by utilizing the volume change caused by the gas-liquid phase change process, so that the defect of high energy consumption of the traditional thermoelectric power generation cold sea water pump is overcome. Secondly, the device widens the functional range of the mooring structure, and the mooring structure is used as a transport guide rail of the cold energy transport bin at the same time to restrict the ascending and descending route of the cold energy transport bin and ensure the reliability and safety of cold energy transport. The device realizes that the liquid phase change material is pushed to enter a cold-required component in a closed power generation thermodynamic cycle structure by utilizing the supercharging positive feedback in the phase change process by arranging the upper magnetic attraction interface and the lower magnetic attraction interface on the surface of the cold energy transport bin, and the power consumption of the cold source pump is reduced to the maximum. Meanwhile, by arranging a plurality of cold energy transporting bins which work alternately on the transporting guide rail, the time interval of the thermodynamic cycle power generation process is shortened. And finally, the device generates electricity based on a closed power generation thermodynamic cycle structure, the generated electric energy is stored in a storage battery, and the electric energy is supplied to an autonomous underwater cruiser working in deep sea through a magnetic charging port. The device can eliminate the defect that the power supply distance is limited by the length of the submarine cable, and has good concealment.
The multifunctional anchor system structure comprises a mooring rope, an anchorage concrete block and a conveying guide rail; the anchorage concrete block is fixed on the sea bottom and is connected with the power generation bin through the mooring rope to play a role in positioning; the mooring ropes are fixed relative to the conveying guide rails, a fixed running track is provided for the cold energy conveying bin, and the ascending and descending route of the cold energy conveying bin is restrained.
The electric energy generated by the power generation bin is stored in the storage battery, and the electric energy is supplied to the autonomous underwater vehicle through the magnetic attraction charging interface of the power generation bin.
The working medium used in the closed loop can be, but not limited to, low-boiling-point pure working medium or mixed working medium such as R245fa, R134a, R1233zd (E), ammonia water and the like.
The buoyancy of the cold energy transportation bin can be changed through the volume change of the elastic oil bag, so that the unpowered ascending and submerging of the cold energy transportation bin under water is realized.
The heat preservation layer of the cold energy transport bin is of a sandwich structure, is respectively an anti-corrosion, heat preservation and waterproof layer from inside to outside, and can be made of the following materials with corresponding functions, such as but not limited to outer neoprene, middle polyvinyl chloride foam and inner polyurethane.
The gas-liquid phase change material is stored in the gas-liquid phase change cavity, the saturation temperature of the gas-liquid phase change material is 4-8 ℃, the gas-liquid phase change material is condensed by exchanging heat with deep cold sea water in the Leng Hai water pipeline, the liquid gas-liquid phase change material can be released into the condenser through the magnetic interface(s), the liquid gas-liquid phase change material exchanges heat with the working medium in the condenser to realize the evaporation of the gas-liquid phase change material, and the periodic evaporation-condensation process realizes the transportation of cold energy from the sea floor to the sea surface.
The gas-liquid phase change material may be, but is not limited to, the following: organic working media such as R134a, R245fa and the like, inorganic working media such as water, ammonia and the like and other mixed working media; the phase change pressure of the gas-liquid phase change material is determined by the filling pressure in the balance pressure cavity.
The balance pressure chamber is filled with gas such as dry air, nitrogen, helium, etc. with density insensitive to temperature, but not limited to the above gases.
When the cold energy conveying bin descends to a certain depth (about 800 m), the pressure-sensitive valve is opened, cold sea water enters the phase-change material cavity to exchange heat with the gas-liquid phase-change material under the action of sea water pressure, the gas-liquid phase-change material evaporates, expands in volume, pushes the upper piston with a rack to move, drives the gear to rotate, the gear further drives the lower piston with the rack to move, compresses the oil storage bin, oil stored in the oil storage bin enters the elastic oil bag through the communicating port, the volume of the elastic oil bag expands, the volume of the cold energy conveying bin increases, the buoyancy increases, and floats upwards, and cold energy is brought into the ocean surface layer from the ocean floor.
The closed power generation thermodynamic cycle structure can be used for generating power thermodynamic cycles suitable for working conditions of low temperature difference and low evaporation temperature, such as organic Rankine cycle, kalina cycle and the like.
The cold energy transporting bin and the multifunctional anchor system structure can be arranged on the transporting guide rail according to actual conditions, the cold energy transporting bin floats on the left side rail, and the cold energy transporting bin is submerged on the right side rail after the cold energy transferring process is completed. After the former cold energy transporting bin finishes cold energy transfer, the latter cold energy transporting bin is in butt joint with an energy transferring port of the power generating bin, so that the time interval of the thermal cycle power generating process is shortened in the working process of alternately floating-working-submerging-storing.
Through the technical scheme, compared with the prior art, the invention has the following beneficial effects:
1. the invention utilizes renewable ocean temperature difference energy as driving energy, and provides an ocean temperature difference energy power generation device capable of being arranged under water, which spontaneously generates electric energy and stores the electric energy in a battery to provide electric energy for an autonomous underwater cruiser without relying on long-distance electric energy transmission on land or shore charging;
2. aiming at the problem that the mode of transporting cold sea water through a pipeline has higher consumption, the invention provides an unpowered driving submersible cold sea water transporting bin, which can utilize the volume change of a gas-liquid phase change material in the periodic evaporation-condensation process between ocean surface layer temperature sea water and deep cold sea water and transmit the volume change to an elastomer, so as to realize the volume change of the cold sea water transporting bin, further realize the buoyancy change of the cold sea water transporting bin and realize unpowered submersible.
3. Aiming at the problems of track, communication and cold energy transfer of cold energy transport equipment in practical application, the invention provides a multifunctional anchor system structure and a main and auxiliary body butt joint structure, wherein the anchor system structure is used as a transport guide rail of an unpowered lifting and diving cold energy transport bin at the same time, so as to restrict the lifting and diving route of the cold energy transport bin and ensure the reliability and safety of cold energy transport; meanwhile, the provided double-magnetic interface type butt joint structure can utilize the phase change process to boost positive feedback to push the liquid phase change material to enter a cold-required component in the closed power generation thermodynamic cycle structure, so that the power consumption of a cold source pump is reduced to the maximum extent, and the net output power of the power generation device is improved.
4. Aiming at the problems of strong intermittence and low time efficiency of the ocean temperature difference energy power generation system caused by long working cycle time consumption of the cold energy transportation bin, the invention provides a problem solving idea of pipelining cold energy transportation. A plurality of cold energy transporting bins can be arranged on the transporting guide rail, the cold energy transporting bins float on the left side rail, and the right side rail is submerged after the cold energy transferring process is completed. After the former cold energy transporting bin finishes cold energy transfer, the latter cold energy transporting bin is in butt joint with an energy transferring port of the power generating bin, so that the time interval of the thermodynamic cycle power generating process is shortened in the working process of alternately floating, working, submerging and storing, and the purpose of improving the power generating time efficiency of the device is achieved.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and other drawings may be obtained according to the structures shown in these drawings without inventive effort for a person skilled in the art. In the drawings:
FIG. 1 is a schematic view of the overall structure of the present invention;
FIG. 2 is a schematic diagram of the unpowered ascending and diving cold energy transporting bin structure of the present invention;
FIG. 3 is a schematic view of the gear drive configuration in the cold energy transport bin of the present invention;
FIG. 4 is a schematic diagram of a pipelined cold energy transport mode of operation of the present invention;
FIG. 5 is a schematic view of a transport track in a multi-functional anchor structure of the present invention;
FIG. 6 is a schematic diagram of the structure of an organic Rankine cycle power generation cartridge according to an embodiment of the present invention;
fig. 7 is a schematic structural diagram of a kalina cycle power generation bin according to an embodiment of the present invention;
fig. 8 is a temperature entropy diagram of an organic rankine cycle according to an embodiment of the invention;
fig. 9 is a kalina cycle temperature entropy diagram of an embodiment of the present invention;
wherein: 1-a power generation bin; 101-a pressure resistant bin; 102-warm seawater inlet; 103-a warm seawater outlet; 1041-a magnetic interface; 1042-magnetic interface; 105-a cold source pump; 106, a cold source pipeline; 107-a condenser; 108-working medium pipelines; 109-working medium pump; 110-a heat source conduit; a 111-evaporator; 112-turbine; 113-turbine main shaft; 114-generator; 115-a battery; 116-a magnetic charging port; 117-cable; 118-separator; 119-regenerator; 120-throttle valve; 121-a mixer; 2-a heat source pump; 3-a cold energy transportation bin; 301-a pressure housing; 3021-a magnetic interface; 3022-a magnetic interface; 303-a cold source inlet with a pressure-sensitive valve; 304-a cold source outlet with a pressure-sensitive valve; 305, an insulating layer; 3051-waterproof layer; 3052-insulating layer; 3053-an anti-corrosion layer; 306-cold seawater flow passage; 307-gas-liquid phase change chamber; 3081-a piston with rack; 3082-a piston with a rack; 309-balance pressure chamber; 310-an oil storage cavity; 311-connecting ports; 312-elastic oil sacs; 313-gear; 401-anchoring a concrete block; 402-mooring lines; 403-transport tracks; 4031-mooring noose; 4032-slide rails; 4033-a spherical pulley; 4034-a connecting rod; 404-mooring clasp; 501-seabed; 502-sea surface; 503-autonomous underwater cruise; 6-working medium saturation line/basic ammonia-water mixture saturation line; 7-working medium workflow lines; 8-a warm seawater energy release curve; 9-gas-liquid phase material release/storage curve; 10-cold seawater energy release curve; 11-lean ammonia working medium saturation line; 12-an ammonia-rich working medium saturation line; s1, an evaporator working medium inlet state point; s2, a working medium saturated gaseous point in the evaporator; s3, an evaporator working medium outlet state point; s4, a condenser working medium inlet state point; s5, a condenser working medium outlet state point; s6, working medium pump working medium outlet state points; s7, an evaporator temperature sea water inlet state point; s8, an evaporator temperature sea water outlet state point; s9, a condenser gas-liquid phase material inlet state point; s10, a condenser gas-liquid phase material outlet state point; s11, a cold sea water inlet state point; s12, a cold sea water outlet state point; r1 is an evaporator working medium outlet state point; r2-the outlet state point of the ammonia-rich working medium of the separator; r3-the outlet state point of the ammonia-rich working medium of the turbine; r4-the lean ammonia working medium outlet state point of the separator; r5 is a state point of an ammonia-lean working medium inlet of the throttle valve; r6 is a state point of an ammonia-lean working medium outlet of the throttle valve; r7 is the working medium outlet state point of the mixer; r8 is the working medium outlet state point of the condenser; r9 is the working medium pump outlet state point; r10 is the working medium inlet state point of the evaporator; r11 is the evaporator temperature sea water inlet state point; r12 is the outlet state point of the evaporator temperature sea water; r13-the inlet status point of the condenser gas-liquid phase-change material; r14-the condenser gas-liquid phase material exit point; r15 is a cold sea water outlet state point; r16-cold sea water inlet status point.
Detailed Description
The present invention will be further described in detail with reference to the drawings, which are only for the purpose of illustrating the invention and are not to be construed as limiting the scope of the invention.
Fig. 1 shows the overall structure of an energy-storage type ocean temperature difference energy underwater conversion device, which comprises a power generation bin 1, a heat source pump 2, a cold energy transportation bin 3 and a multifunctional anchor system structure, wherein the power generation bin 1, the heat source pump 2, the cold energy transportation bin 3 and the multifunctional anchor system structure are arranged below the sea level. The power generation silo 1 is connected in an anchorage concrete block 401 fixed on the sea bottom through a mooring rope 402 to play a role in positioning. The heat source pump 2 is connected with the power generation bin 1 through the warm seawater inlet 103, the cold energy transport bin 3 is connected with the magnetic suction interface 104 of the power generation bin through the two magnetic suction interfaces 302 in the sea surface cold release process, and after the cold energy release is completed, the magnetic suction interfaces 302 are separated, and the cold energy transport bin is sunk into the sea bottom along the mooring rope 402 to store cold again; the power generation bin 1 realizes the in-situ capturing conversion of ocean temperature difference energy under the driving of the ocean surface sea water and the temperature difference of the cold energy carried by the cold energy power generation bin. The electric energy generated by the power generation bin 1 is stored in the storage battery 115, and power supply is provided for the autonomous underwater vehicle through the magnetic attraction charging port 116 of the power generation bin 1.
Figure 2 illustrates an unpowered ascending latent cold energy transportation silo structure. Comprises a pressure-proof shell 301, a magnetic attraction interface 302, a pressure-sensitive valve 303, a heat preservation layer 305, a cold sea water flow channel 306, a gas-liquid phase cavity 307, a piston 308 with a rack, a balance pressure cavity 309, an oil storage cavity 310, a communication port 311, an elastic oil bag 312 and a gear 313. The left side of the upper piston 308 is provided with low-boiling-point gas-liquid phase-change material, the right side is nitrogen, the left side of the lower piston 308 is nitrogen, the right side is hydraulic oil, and the inside of the elastic oil bag 312 is filled with low-density hydraulic oil. The pressure-resistant housing 301 is divided into three layers, namely a neoprene anticorrosive layer 3051, a polyvinyl chloride foam heat-insulating layer 3052 and a molded polyurethane waterproof protective layer 3053, so as to achieve the effects of anticorrosion, heat preservation and waterproof. The inlet and outlet of the sea water pipeline are provided with pressure sensitive switches 303, and when the surface pressure reaches a threshold value, the pipeline is opened.
Fig. 3 shows the principle of action of the gear 313 in the unpowered ascending latent cold energy transportation silo 3 on the piston 308. The gear 313 is connected to a rack, which is fixed to the piston 308 on one side, in front and rear, respectively. When the upper piston 308 moves, the piston 308 moves the rack fixed thereto, and the lower piston 308 and the rack connected thereto move in opposite directions due to the presence of the gear 313. In practical applications, the magnitude of movement may be controlled by the size and number of gears 313 and racks.
Fig. 4 illustrates the principle of operation of the pipelined mechanism for transporting cold energy. The mooring structure is connected to the power generation silo by means of mooring buckles 404. The transport rail 403 is divided into a left floating rail, a right submerged rail, and a connecting rail in the middle, and a certain height difference is formed between the top end of the floating rail and the top end of the submerged rail. A plurality of cold energy transporting cabins 3 are distributed on the transporting rail 403, the cold energy transporting cabins 3 float on the left rail, after the cold energy transferring process is completed, the repulsive force is released by the power generating cabin 101 through the magnetic attraction interface 1041 and the magnetic attraction interface 1042, and the cold energy transporting cabins 3 are pushed to move to the right side to enter the submerged rail through the connecting rail. After the former cold energy transporting bin finishes cold energy transfer, the latter cold energy transporting bin is in butt joint with an energy transferring port of the power generating bin, so that the time interval of the thermodynamic cycle power generating process is shortened in the working process of alternately floating, working, submerging and storing, and the purpose of improving the power generating time efficiency of the device is achieved.
Fig. 5 shows a specific structure of the transportation rail in the multi-functional anchor structure. Including mooring loops 4031, rails 4032, ball pulleys 4033 and links 4034. The mooring rope sleeve 4031 is fixed on the back of the sliding rail 4032, the mooring rope 402 passes through the mooring rope sleeve 4031 to be fixed with the conveying rail 403, the cold energy conveying bin 3 is connected with the spherical pulley 4033 through the connecting rod 4034, and the spherical pulley 4033 can freely move in the sliding rail 4032 to realize the floating and submerging movement of the cold energy conveying bin 3.
Fig. 6 shows the structure of the ocean thermal energy organic rankine cycle power generation bin 1 in the embodiment. The power generation bin 1 takes organic Rankine cycle as a basic configuration, takes single organic matters or mixed organic matters as working media, and generates electric energy by utilizing the temperature difference energy between the heat energy carried by the surface-temperature seawater and the cold energy carried by the cold energy transportation bin. Specifically, the power generation bin comprises a pressure-resistant bin 101, a warm seawater inlet 102, a warm seawater outlet 103, a magnetic attraction interface 104, a cold source pump 105, a cold source pipeline 106, a condenser 107, a working medium pipeline 108, a working medium pump 109, a heat source pipeline 110, an evaporator 111, a turbine 112, a turbine main shaft 113, a generator 114, a storage battery 115, a magnetic attraction charging port 116 and a cable 117; cold source pump 105, condenser 107, working medium pump 109, evaporator 111, turbine 112, generator 114, accumulator 115, heat source pipe 110, cold source pipe 106, working medium pipe 108, and cable 117 are packaged in pressure-resistant bin 101; the condenser 107, the working medium pump 109, the evaporator 111 and the turbine 112 are connected through a working medium pipeline to form a closed turbine power generation thermodynamic cycle; the warm sea water inlet 102, the heat source pipeline 110 and the evaporator 111 are connected with the warm sea water outlet 102 to form an energy release path of heat energy carried by warm sea water; the magnetic interface 1041, the cold source pump 105, the condenser 107 and the magnetic interface 1042 form an energy release path of the cold energy carried by the cold energy transport bin 3; the turbine main shaft 113 is connected with the rotor of the generator 114; the generator 114, the storage battery 115 and the magnetic charging port 116 are connected by a cable 117.
Fig. 7 shows the structure of the ocean thermal energy kalina cycle power generation bin 1 in the embodiment. The power generation bin 1 takes a kalina cycle as a basic configuration, takes an ammonia-water mixture as a working medium, and utilizes the temperature difference energy between the heat energy carried by the surface-temperature seawater and the cold energy carried by the cold energy transportation bin to generate electric energy. Specifically, pressure-resistant bin 101, warm seawater inlet 102, warm seawater outlet 103, magnetic interface 104, cold source pump 105, cold source pipeline 106, condenser 107, working medium pipeline 108, working medium pump 109, heat source pipeline 110, evaporator 111, turbine 112, turbine main shaft 113, generator 114, accumulator 115, magnetic charging port 116, cable 117, separator 118, regenerator 119, throttle valve 120, and mixer 121; cold source pump 105, condenser 107, working medium pump 109, evaporator 111, turbine 112, generator 114, battery 115, heat source pipe 110, cold source pipe 106, working medium pipe 108, cable 117, separator 118, regenerator 119, throttle valve 120, mixer 121 are packaged in pressure-resistant bin 101; the condenser 107, the working medium pump 109, the evaporator 111, the separator 118, the turbine 112, the mixer 121, the throttle valve 120 and the heat regenerator 119 are connected through the working medium pipeline 108 to form a closed turbine power generation thermodynamic cycle; the warm sea water inlet 102, the heat source pipeline 110 and the evaporator 111 are connected with the warm sea water outlet 103 to form an energy release path of heat energy carried by the warm sea water; the magnetic interface 104, the cold source pump 105, the condenser 107 and the magnetic interface 104 form an energy release path of cold energy carried by the cold energy transport bin 3; the turbine main shaft is connected with the generator rotor; the generator 114, the storage battery 115 and the magnetic charging port 116 are connected by a cable 117.
The specific working procedure of the above embodiment is as follows:
as shown in figure 1, the energy-storage type ocean temperature difference energy underwater conversion device directly extracts surface-temperature seawater as a heat source, uses a low-boiling-point phase-change material in the unpowered ascending and submerged cold energy transportation bin as a cold source, and utilizes the temperature difference between the surface-temperature seawater and the phase-change material to drive a closed power generation thermodynamic cycle structure to generate power. The sea water temperature tends to decrease with increasing vertical depth. In south China sea, the temperature of surface sea water (0-50 m below sea level) is kept above 25 ℃ throughout the year, and the temperature of deep sea water (600 m below) is kept below 7 ℃ throughout the year.
The energy storage type ocean temperature difference energy underwater conversion device adopts an organic Rankine cycle or a kalina cycle to generate power, and the specific process is as follows:
the structure of the power generation bin of the energy storage type ocean temperature difference energy underwater conversion device adopting the organic Rankine cycle power generation is shown in figure 4. After entering the heat source pipeline 110 from the warm sea water inlet 102, the surface-layer warm sea water enters the evaporator 111 to exchange heat with the circulating working medium, heats and evaporates the circulating working medium into a gas phase, and finally is discharged into the sea water through the warm sea water outlet 103. The circulating working medium is evaporated into high-temperature and high-pressure gas in the evaporator 111, then enters the turbine 112, pushes the turbine impeller to do work and then becomes low-temperature and low-pressure gas, then enters the condenser 107, exchanges heat with the low-temperature phase change material and becomes low-temperature and low-pressure liquid, and then enters the evaporator 111 again after being pressurized by the working medium pump 110, thus forming a power generation cycle.
The structure of the power generation bin of the energy storage type ocean temperature difference energy underwater conversion device adopting the kalina cycle power generation is shown in figure 5. After entering the heat source pipeline 110 from the warm sea water inlet 102, the surface layer warm sea water enters the evaporator 111 to exchange heat with the circulating working medium ammonia-water mixed liquid, heats and evaporates the circulating working medium into a gas phase, and finally is discharged into sea water through the warm sea water outlet 103. The heat exchanged ammonia-water working medium enters the separator 118 for separation, and the separated working medium becomes ammonia-rich steam and ammonia-poor working medium. The ammonia-rich steam enters a turbine 112 to generate electricity, the lean ammonia working medium enters a heat regenerator 119 to preheat the ammonia-water working medium, the preheated lean ammonia working medium enters a throttle valve 120 to reduce pressure, the lean ammonia working medium and the exhaust steam of the turbine are mixed in a mixer 121 and enter a condenser 107, the ammonia-water mixture is condensed by the condenser 107 and then enters a working medium pump 109 to be boosted, and then enters the heat regenerator 119 to preheat, so that the electricity generation cycle is formed.
The specific process of conveying cold energy by the unpowered ascending and submerged cold energy conveying bin 3 of the energy storage type ocean temperature difference energy underwater conversion device is as follows:
the energy storage type ocean temperature difference energy underwater conversion device adopts an operating mode of utilizing the volume change to cause buoyancy change so as to realize cold energy transportation, as shown in figure 2. The mating structure of the inner piston 308 and the gear 313 is shown in fig. 3. When the liquid phase change material is expanded into a gas phase by heat exchange with the circulating working medium in the condenser 107, the volume is enlarged, the pressure is increased, the upper piston 308 moves rightwards under the action of air pressure, the upper piston 308 drives the rack connected with the upper piston 308 to move rightwards together, the lower piston 308 and the rack connected with the lower piston move towards the opposite direction due to the existence of the gear 313, negative pressure is formed in the right cavity below the lower piston, hydraulic oil in the elastic oil bag 312 is attracted to flow to the cavity, the elastic oil bag 312 contracts, the buoyancy of the whole cold energy transport bin 3 is reduced, the constraint is released after the energy release process is completed, and the hydraulic oil is sunk to the seabed along the transport guide rail to complete energy storage. When the cold energy transportation bin 3 descends to a certain depth, the pressure of the seawater on the seawater pipeline in the cold energy transportation bin 3 reaches a threshold value, the seawater pipeline is opened, and the seawater enters the cold seawater flow passage 306 to cool the cold storage phase change material. Similarly, after the cold storage process is completed, the elastic oil bag 312 is inflated and the cold energy transporting bin 3 floats up along the transporting rail, thereby forming a cycle.
The specific working process of the cold energy transport bin for transmitting cold energy to the condenser is as follows:
when the cold energy transporting bin 3 floats up to the pressure resistant bin 101 and is detected by the infrared sensing system, the control system of the pressure resistant bin 101 starts to act, the electromagnetic relay is started to fix the cold energy transporting bin 3 by magnetic force, the butt joint of the energy conveying port 302 and the energy conveying pipeline is completed by utilizing a specific mechanical structure, the cold source pump 105 starts to work, the liquid phase change material in the gas-liquid phase change bin 307 is sucked through the lower energy conveying port, the phase change material enters the condenser, and the residual gas phase change material in the condenser is pressed into the gas-liquid phase change bin 307 from the upper energy conveying port. Meanwhile, the liquid phase change material entering the condenser is heated and evaporated into gas, the interior of the condenser 107 is further pressurized, the gas phase change material is pressed into the gas-liquid phase change bin 307 from the upper energy transmission port, positive feedback pushes the phase change material to enter the condenser 107, and the power consumption of the cold source pump 105 for completing the cold energy transmission process is greatly reduced. After the cold energy transfer process is completed, the phase change material in the cold energy transportation bin 3 is completely evaporated, the overall pressure of the condenser-cold energy transportation bin system is increased, a small part of the gas phase change material remains in the condenser 107, and a large part of the gas phase change material returns to the cold energy transportation bin 3 to complete the next energy storage process, so that a cycle is formed.
Taking the south sea area as an example, as shown in fig. 1, a power generation bin 101 of the energy storage type ocean temperature difference energy underwater conversion device is suspended in surface sea water under the action of mooring ropes 402 and anchorage concrete blocks 401. The surface-temperature seawater is pumped by the heat source pump 102, and the cold energy of the deep cold seawater is stored by the cold energy transportation bin 3. The warm seawater pumped by the heat source pump 102 enters the evaporator 111, the temperature of the warm seawater at the inlet is 28 ℃, the water temperature of the cold seawater is 4 ℃, the phase change temperature of the phase change material used in the cold energy transportation bin 3 is 6 ℃, the heat exchange temperature difference of the cold energy transportation bin 3 is 1 ℃, the temperature of the phase change material is 1 ℃ in the transportation process, and the temperature of the phase change material entering the condenser 111 is 6 ℃.
In this embodiment, the thermodynamic cycle process will be illustrated by taking an organic rankine cycle and a kalina cycle as alternatives of a closed power generation thermodynamic cycle structure, respectively.
The organic Rankine cycle is used as a design scheme of a closed power generation thermodynamic cycle structure, and the thermodynamic cycle process is as follows:
according to the actual working condition, R134a is adopted as a circulating working medium of the power generation thermodynamic cycle of the energy storage type ocean temperature difference energy underwater conversion device, and the circulating working medium can be, but is not limited to, R134a. The circulating working medium R134a exchanges heat with the surface-layer warm seawater at 28 ℃ in the evaporator 111, the warm seawater releases heat, the temperature drops to 24 ℃, and R134a is heated to be overheated gas; the heated and evaporated R134a gaseous working medium drives the turbine 112 to rotate at high speed and drives the generator 114 to generate electric energy; the outlet exhaust gas exchanges heat with a cold-carrying phase-change medium R245fa at the temperature of 6 ℃ in a condenser 107 (the pressure in a cold energy transport bin is designed to be 0.069 MPa), the cold-carrying phase-change medium R245fa absorbs heat to generate phase change, the temperature is unchanged in the phase change process, and R134a is condensed into a saturated liquid state; the working medium pump 109 drives the liquid R134a to enter the evaporator 111 to be heated, phase-changed and expanded into gas, so as to complete one working medium cycle. The temperature entropy diagram of the working medium cycle is shown in FIG. 6, where the evaporator 111 and condenser 107 are at a pinch temperature differential ΔT PP1 And DeltaT PP2 2 ℃ and 5 ℃ (respectively) ensure that the cold-loaded phase change medium can undergo phase change. When other irreversible losses except irreversible losses caused by heat exchange of the system are not counted, thermodynamic parameters of all state points on the temperature entropy diagram are obtained through the state parameters of the R134a working medium, and the thermodynamic parameters are shown in table 1.
Table 1: thermodynamic parameters for cycling state points on an organic Rankine cycle temperature entropy diagram
From the thermodynamic parameters of Table 1, it is known that single-site quality working substance R134a absorbs heat ΔQ in evaporator 111 e Ideal enthalpy drop Δh for turbine inlet and outlet (198.15 kJ/kg) 1 =8.48 kJ/kg, condenser 107 exotherm Δq c = 189.93kJ/kg, setting the generator 114 output power P w =1 kW, turbine efficiency η w =85%, mechanical efficiency η m =98%, generator efficiency η p =93%, so the required mass flow of the cycle working medium R134a is 0.15kg/s. Further, the heat absorption amount in the evaporation process in the evaporator is 30.16kW, and the heat release amount in the condensation process is 28.91kW. In the design process, the temperature difference delta T of the inlet and outlet of the warm seawater in the evaporator is 4 ℃, and the mass flow of the warm seawater required by the evaporator 111 is 1.70kg/s according to calculation.
In the embodiment, R245fa is adopted as a cold storage medium of the cold energy transport bin 3, the design pressure is 0.069MPa, the phase transition temperature is 6 ℃, and the phase transition latent heat is 201.18kJ/kg. The design of the cold carrier single cycle can bear 50kg of cold storage medium, and the first stage of single power generation can last for 347.94s approximately, and the total power generation can generate 347.94 kJ.
In order to obtain the net output electric power of the energy-storage type ocean temperature difference energy underwater conversion device, the system consumption is deducted, and the system consumption comprises a working medium pump 109, a heat source pump 2, a cold source pump 105 and a control system consumption. The working fluid pump 109 is mainly used for conveying working fluid and lifting working fluid pressure heads, and the total energy delta H obtained by the single-position working fluid passing through the working fluid pump 109 can be known according to the table 1 p =0.26 kJ/kg, working fluid pump 111 efficiency η is set p =0.75 to obtain the total power consumption W of the working medium pump p = 0.0528kW. The power consumption of the heat source pump 2 is based onCalculation of Q v Is the delivered fluid volumetric flow rate, Δp is the total resistance, η is the pump efficiency, η=0.8,seawater side flow resistance P of evaporator 111 hex Is 1kPa. Length of warm sea water pipeline l w =20m, select warm sea water pipe inside diameter D 1 =0.1m, the resistance along the way isLocal resistance loss is according to->Calculating to obtain the local resistance loss P w2 =231 Pa, total resistance to be overcome by the seawater pump 102 is P wp ＝P w1 +P w2 +P hex ＝
1243Pa, power consumption W wp 0.024kW; so the self-consumption W of the closed power generation thermodynamic cycle system designed in the embodiment pu ＝W wp +W p = 0.0768kW, the power output to the battery 115 is 0.9232kW. The power consumption of the single circulation control system is set to be 10kJ, and the total power consumption of the cold source pump 105 for pumping the phase change cold storage medium R245fa in the single circulation is set to be 1kJ. Therefore, the total power consumption in the power generation stage is 37.72kJ, and the total net power is 310.22kJ.
The design scheme of taking the kalina cycle as a closed power generation thermodynamic cycle structure comprises the following thermodynamic cycle process embodiments:
according to the actual working condition, the ammonia-water mixture with the mass concentration of 95% is adopted as the circulating working medium of the power generation thermodynamic cycle of the energy storage type ocean temperature difference energy underwater conversion device. The ammonia-water mixture is evaporated in the evaporator 111 by heat exchange with the surface layer temperature seawater at 28 ℃, the temperature seawater releases heat, the temperature is reduced to 24 ℃, the ammonia-water mixture is heated to a gas-liquid mixture at 26 ℃, and the pressure is 0.9MPa; the heated vaporized gaseous ammonia-water mixture enters separator 118 to be separated into ammonia rich vapor and ammonia lean solution. The ammonia-rich vapor drives turbine 112 to rotate at a high speed to drive generator 114 to generate electricity, and the ammonia-lean solution enters regenerator 119 to preheat the ammonia-water mixture to be fed into evaporator 111. The low temperature and low pressure ammonia-rich vapor at the outlet of the turbine 112 is mixed with the ammonia-lean solution cooled by the regenerator 119 and throttled by the throttle valve 120 in the mixer 121, and the mixed ammonia-water mixture is transported by cold energy in the condenser 1073, the pure liquid phase ammonia-water mixture after cooling is boosted by the working medium pump 109 and heated by the heat regenerator 119, and then enters the evaporator 111 again to absorb heat and evaporate, thus forming circulation. The temperature entropy diagram of the working medium cycle is shown in FIG. 7, where the evaporator 111 and condenser 107 are at a pinch temperature differential ΔT PP1 And DeltaT PP2 2 ℃ and 5 ℃ (respectively) ensure that the cold-loaded phase change medium can undergo phase change. Thermodynamic parameters of each state point of the circulation on the temperature entropy diagram are obtained through the ammonia-water working substance state parameters when other irreversible losses except the irreversible losses caused by heat exchange of the system are not counted, and are shown in table 2.
Table 2: thermodynamic parameters of each state point of cycle on kalina cycle temperature entropy diagram
From the thermodynamic parameters of Table 2, it is known that the single-unit quality working medium ammonia-water mixture absorbs heat ΔQ in evaporator 111 e Ideal enthalpy drop Δh for turbine inlet and outlet (767.22 kJ/kg) 1 = 37.72kJ/kg, condenser 107 exotherm Δq c = 744.46kJ/kg, setting the generator 114 output power P w =1 kW, turbine efficiency η w =85%, mechanical efficiency η m =98%, generator efficiency η p =93%, so the mass flow of the required cycle working medium ammonia-water mixture is 0.034kg/s. Further, the heat absorption capacity in the evaporation process in the evaporator is 26.255kW, and the heat release capacity in the condensation process is 25.312kW. In the design process, the temperature difference delta T of the inlet and outlet of the warm seawater in the evaporator is 4 ℃, and the mass flow of the warm seawater required by the evaporator 111 is 1.60kg/s according to calculation.
In the embodiment, R245fa is adopted as a cold storage medium of the cold energy transport bin 3, the design pressure is 0.069MPa, the phase transition temperature is 6 ℃, and the phase transition latent heat is 201.18kJ/kg. The design of the cold carrier single cycle can bear 50kg of cold storage medium, and the first stage of single power generation can last for 397.40s approximately, and the total power generation can generate 397.40 kJ.
In order to obtain the net output electric power of the energy-storage type ocean temperature difference energy underwater conversion device, a buckle is neededExcept for system consumption, including working fluid pump 109, heat source pump 2, cold source pump 105, and control system power consumption. The working fluid pump 109 is mainly used for conveying working fluid and lifting working fluid pressure heads, and the total energy delta H obtained by the single-position working fluid passing through the working fluid pump 109 can be known according to the table 1 p =0.46 kJ/kg, working fluid pump 111 efficiency η is set p =0.75 to obtain the total power consumption W of the working medium pump p =0.0209 kW. The power consumption of the heat source pump 2 is based onCalculation of Q v Is the volumetric flow rate of the delivery fluid, Δp is the total resistance, η is the pump efficiency, η=0.8, and the seawater side flow resistance P of the evaporator 111 is taken hex Is 1kPa. Length of warm sea water pipeline l w =20m, select warm sea water pipe inside diameter D 1 =0.1m, the resistance along the way isLocal resistance loss is according to->Calculating to obtain the local resistance loss P w2 The total resistance to be overcome by the seawater pump 102 is P = 203.28Pa wp ＝P w1 +P w2 +P hex 1213.84Pa, power consumption W wp 0.022kW; so the self-consumption W of the closed power generation thermodynamic cycle system designed in the embodiment pu ＝W wp +W p = 0.0429kW, the power output to the battery 115 is 0.9571kW. The power consumption of the single circulation control system is set to be 10kJ, and the total power consumption of the cold source pump 105 for pumping the phase change cold storage medium R245fa in the single circulation is set to be 1kJ. Therefore, the total power consumption in the power generation stage is 28.05kJ, and the total net power is 369.35kJ.
The embodiment of the invention shows specific design technical parameters of closed power generation thermodynamic cycle in the power generation bin 1 of the energy storage type ocean temperature difference energy underwater conversion device, the design technical parameters can be but are not limited to the embodiment, and a low-boiling-point organic working medium with better performance can be selected in the design process to form a power generation cycle with higher efficiency.
The invention aims to provide an energy storage type ocean temperature difference energy underwater conversion device taking an unpowered ascending and diving cold energy transportation bin as a core, which is suitable for energy supply of an autonomous underwater vehicle and can automatically, reliably and stably generate electric energy; the charging and discharging of the power storage module and the autonomous connection and cooperation of the cold energy transportation bin are controlled through the ocean temperature difference energy power generation and automatic control technology; through the application of the variable volume cold energy transportation bin and the auxiliary technology thereof, the large power consumption generated by long-distance transportation of cold sea water is avoided, and the realizability of ocean temperature difference energy power generation is improved to a greater extent.
The foregoing detailed description will set forth only for the purposes of illustrating the general principles and features of the invention, and is not meant to limit the scope of the invention in any way, but rather should be construed in view of the appended claims.
Claims (10)
1. An energy-storage type ocean temperature difference energy underwater conversion device is characterized by comprising:
a heat source pump for providing ocean surface temperature seawater;
the cold energy transport bin is used for providing deep ocean cold sea water; the cold energy transportation bin comprises a gas-liquid phase change cavity, an oil storage cavity and an elastic oil bag, and the oil storage cavity is communicated with the elastic oil bag; the gas-liquid phase change cavity comprises a phase change material cavity and a first balance cavity, and the oil storage cavity comprises an oil cavity and a second balance cavity; a linkage mechanism is arranged between the gas-liquid phase-change cavity and the oil storage cavity, and the linkage mechanism synchronously increases or reduces the volume of the oil cavity when the volume of the phase-change material in the phase-change material cavity is increased or reduced due to the volume change in the evaporation-condensation process of the phase-change material; when the volume of the oil cavity is increased, the elastic oil bag is contracted, and the buoyancy of the cold energy transportation bin is reduced; when the volume of the oil cavity is reduced, the elastic oil bag is increased, and the buoyancy of the cold energy transportation bin is increased;
the power generation bin is used for generating power and storing by utilizing the temperature difference between the ocean surface layer temperature seawater provided by the heat source pump and the ocean deep cold seawater provided by the cold energy transportation bin;
and
And the multifunctional anchoring structure anchors the power generation bin on the seabed and provides a running track for the cold energy transportation bin.
2. The energy storage type ocean temperature difference energy underwater conversion device according to claim 1, wherein the multifunctional anchor system structure comprises mooring ropes, anchor concrete blocks and conveying guide rails; the anchorage concrete block is fixed on the sea bottom and is connected with the power generation bin through the mooring rope to play a role in positioning; the mooring ropes are fixed relative to the conveying guide rails, a fixed running track is provided for the cold energy conveying bin, and the ascending and descending route of the cold energy conveying bin is restrained.
3. The energy storage type ocean temperature difference energy underwater conversion device according to claim 2, wherein a plurality of cold energy transporting cabins are distributed on the transporting guide rail, and the plurality of cold energy transporting cabins work alternately, so that the time interval between the front power generation process and the rear power generation process is shortened.
4. The energy-storage type ocean temperature difference energy underwater conversion device according to claim 3, wherein the conveying rail is divided into a left floating rail, a right submerged rail and a middle connecting rail, and a height difference exists between the top end of the floating rail and the top end of the submerged rail; the cold energy transport bin floats up along the left floating rail and slides to the submerging rail and submerges at the highest point along the connecting rail due to the height difference.
5. The energy storage type ocean temperature difference energy underwater conversion device according to claim 1, wherein the linkage mechanism comprises an upper piston, a lower piston and a gear, and racks meshed with the gear are respectively arranged on the upper piston and the lower piston; the two sides of the upper piston are respectively provided with the phase change material cavity and a first balance pressure cavity; the two sides of the lower piston are respectively provided with the oil cavity and a second balance pressure cavity; the phase change material chamber is located at the upper piston opposite to the oil chamber is located at the lower piston.
6. The energy-storage type ocean temperature difference energy underwater conversion device according to claim 1, wherein the power generation bin takes turbine power generation thermodynamic cycle as a basic configuration to realize thermal power-thermoelectric conversion of ocean temperature difference energy.
7. The energy storage type ocean temperature difference energy underwater conversion device according to claim 1, wherein the cold energy transportation bin is used for realizing the butt joint with a main body and an auxiliary body of the power generation bin by arranging an upper magnetic attraction interface and a lower magnetic attraction interface; and the liquid phase change material in the components to be cooled in the power generation bin is heated and evaporated into gas, the interior of the components to be cooled is further pressurized, the gas phase change material is pressed into the gas-liquid phase change bin from the upper side magnetic interface, positive feedback pushes the phase change material into the components to be cooled, the liquid phase change material is pushed into the components to be cooled in the power generation thermodynamic cycle structure by utilizing the positive feedback of the pressurization in the phase change process, and the power consumption of the cold source pump is reduced to the greatest extent.
8. The energy storage type ocean temperature difference energy underwater conversion device according to claim 1, wherein the power generation bin comprises a pressure resistant bin, a cold source pump, a closed power generation thermodynamic cycle structure, a storage battery, a heat source pipeline, a cold source pipeline, a working medium pipeline, a cable, a magnetic charging port, a first magnetic interface and a second magnetic interface; the warm seawater inlet of the power generation bin is connected with the heat source pump; the cold source pump, the storage battery, the heat source pipeline, the cold source pipeline, the working medium pipeline, the cable and the closed power generation thermodynamic cycle structure are packaged in the pressure-resistant bin; the heat source pipeline is connected with a heat-required component in the closed power generation thermodynamic cycle structure to form an energy release path of heat energy carried by warm seawater; the first magnetic interface, the cold source pump and the second magnetic interface are connected with a cold-required component in the closed power generation thermodynamic cycle structure to form an energy release path of cold energy carried by the cold energy transport bin; the storage battery and the magnetic charging port are connected with a power generation component in the closed power generation thermodynamic cycle structure through a cable; the magnetic charging port provides power supply for the autonomous underwater vehicle.
9. The energy storage type ocean temperature difference energy underwater conversion device according to claim 8, wherein a conformal groove for placing the cold energy transportation bin is formed in the bottom of the pressure resistant bin, and the first magnetic interface and the second magnetic interface are arranged at the conformal groove; and infrared detection equipment is arranged around the first magnetic interface and the second magnetic interface, and after the infrared detection equipment detects that the cold energy transportation bin is in place, the first magnetic interface and the second magnetic interface are electrified and generate magnetism through signal feedback, so that the first magnetic interface and the second magnetic interface are connected with the cold energy transportation bin, and cold energy transportation bin, a cold source pump and cold energy required components in the closed power generation thermodynamic cycle structure are connected through the cold source pipeline to form a closed cold energy release path.
10. The energy-storage type ocean temperature difference energy underwater conversion device according to claim 8, wherein working medium used in a closed loop of the closed power generation thermodynamic cycle structure is a low-boiling-point pure working medium or a mixed working medium; the low-boiling-point pure working medium is R245fa, R134a, R1233zd (E) or ammonia water; the low-boiling mixed working medium is a mixture of any two or more of R245fa, R134a, R1233zd (E) or ammonia water; the gas-liquid phase change material is stored in the gas-liquid phase change cavity, the saturation temperature of the gas-liquid phase change material is 4-8 ℃, the gas-liquid phase change material is condensed by exchanging heat with deep cold sea water in the Leng Hai water pipeline, the liquid gas-liquid phase change material is released into a cold-required component in the closed power generation thermodynamic cycle structure through the first magnetic interface, the second magnetic interface and the cold source pump, the liquid gas-liquid phase change material exchanges heat with the working medium in the cold-required component in the closed power generation thermodynamic cycle structure to realize the evaporation of the gas-liquid phase change material, and the periodic process of evaporation-condensation realizes the transportation of cold energy from the sea floor to the sea surface; the gas-liquid phase change material is an organic working medium, an inorganic working medium or a mixed working medium, wherein the organic working medium is R134a or R245fa, and the inorganic working medium is water or ammonia; the phase change pressure of the gas-liquid phase change material is determined by the filling pressure in the balance pressure cavity; the gas filled in the balance pressure cavity is dry air with insensitive density to temperature, and the dry air is nitrogen or helium; the heat preservation layer is of a sandwich structure and is respectively provided with an anti-corrosion layer, a heat preservation layer and a waterproof layer from inside to outside; the waterproof layer is made of neoprene, the heat-insulating layer is made of polyvinyl chloride foam, and the anti-corrosive layer is made of polyurethane.
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