Double-water-tank seawater source ice slurry heat pump circulation system for engineering

Abstract

The utility model discloses a double-water-tank seawater source ice slurry heat pump circulation system for engineering, which comprises a supercooled water circulation section, an intermediate medium transition section, a steam compression circulation section and a tail end heating circulation section, and the supercooled water circulation section comprises a primary filtering device, two ice slurry storage devices, a water taking pump, an ice discharging pump and a crystallization promoting device; an ethylene glycol solution with the concentration of 25% serves as a medium of the intermediate medium transition section, and the intermediate medium transition section comprises an expansion tank, a circulating pump and a buffer tank; the steam compression circulation section comprises a compressor, an oil separation device, a liquid storage tank, a filtering device and a throttling valve; the tail end heating circulation section is provided with a heat dissipation device, and circulation between the heat dissipation device and the condensation plate type heat exchanger is completed through a heating circulation pump. According to the seawater source ice slurry heat pump system with the double water tanks, unit shutdown caused by freezing of seawater in the heat exchanger can be avoided, meanwhile, the problem that heat supply of a single-water-tank system is unstable is solved, and the heat supply efficiency of a unit is improved.

Description

Technical Field

[0001] The utility model relates to the technical field of renewable energy, in particular to a double-water-tank seawater source ice slurry heat pump circulation system for engineering. Background Art

[0002] Seawater source heat pump is an effective energy-saving technology. It is a new type of heat pump technology that uses the natural low-grade energy in seawater to achieve winter heating. The water intake temperature is a key factor affecting the normal operation of the water source heat pump system. In the extreme winter environment, the seawater temperature is close to the freezing point. When the seawater exchanges heat with the heat exchanger in the open seawater source heat pump system, the temperature drops, which easily causes ice to form on the heat exchanger pipes and block the pipes, thereby affecting the normal operation of the unit. Moreover, the seawater ice slurry heat pump system is in a shutdown state during the ice slurry storage device ice removal and water intake stages and cannot operate continuously and stably. Therefore, there is an urgent need for a dual-tank seawater source ice slurry heat pump system that can avoid pipe blockage caused by seawater freezing, solve the problem of unstable heating in the single-tank system, and improve the heating efficiency of the unit. Utility Model Content

[0003] The purpose of the present utility model is to overcome the deficiencies in the above-mentioned prior art and to provide a dual-water-tank seawater source ice slurry heat pump system that can avoid unit shutdown caused by seawater freezing in the heat exchanger, while solving the problem of unstable heating in a single-water-tank system and improving the heating efficiency of the unit.

[0004] In order to achieve the above-mentioned purpose, the present invention is realized through the following technical solutions:

[0005] A dual-tank seawater source ice slurry heat pump circulation system for engineering projects includes a subcooled water circulation section, an intermediate medium transition section, a steam compression circulation section, and a terminal heating circulation section. A subcooled plate heat exchanger is connected between the subcooled water circulation section and the intermediate medium transition section, an evaporation plate heat exchanger is connected between the intermediate medium transition section and the steam compression circulation section, and a condensation plate heat exchanger is connected between the steam compression circulation section and the terminal heating circulation section.

[0006] The supercooled water circulation section includes a primary filter device, two ice slurry storage devices, a water intake pump, an ice discharge pump and a crystal promoting device. The primary filter device is connected to the water intake pump, and each ice slurry storage device is connected to the primary filter device, the ice discharge pump and the crystal promoting device in parallel. The pipeline where seawater flows from the ice slurry storage device into the supercooled plate heat exchanger is provided with a supercooled water circulation pump and an ice nucleation filter device. The crystal promoting device is provided on the pipeline where seawater flows from the supercooled plate heat exchanger into the ice slurry storage device.

[0007] The intermediate medium transition section uses a 25% concentration of ethylene glycol solution as the medium, and the intermediate medium transition section includes an expansion tank, a circulation pump and a buffer tank. The expansion tank and the circulation pump are arranged on the pipeline where the medium flows from the subcooling plate heat exchanger to the evaporating plate heat exchanger, and the buffer tank is arranged on the pipeline where the medium flows from the evaporating plate heat exchanger to the subcooling plate heat exchanger;

[0008] The steam compression cycle section includes a compressor, an oil separator, a liquid storage tank, a filter device and a throttle valve, wherein the compressor and the oil separator are arranged on the pipeline from the evaporating plate heat exchanger to the condensing plate heat exchanger, and the liquid storage tank, the filter device and the throttle valve are arranged on the pipeline from the condensing plate heat exchanger to the evaporating plate heat exchanger;

[0009] The terminal heating circulation section is provided with a heat dissipation device, and the circulation between the heat dissipation device and the condensing plate heat exchanger is completed by a heating circulation pump.

[0010] Furthermore, an ice nucleus filtering device is provided in each of the ice slurry storage devices.

[0011] Furthermore, an ethylene glycol solution replenishing device is provided in the intermediate medium transition section.

[0012] Furthermore, an oil return pipe is provided between the front end of the compressor and the oil separation device.

[0013] Furthermore, thermometers are provided on the pipelines of the supercooled water circulation section, the intermediate medium transition section and the terminal heating circulation section.

[0014] Furthermore, the subcooling water circulation section is provided with a pressure gauge, a flow meter and a thermometer at both ends of the subcooling plate heat exchanger.

[0015] Furthermore, the subcooling plate heat exchanger, the evaporating plate heat exchanger and the condensing plate heat exchanger are all plate heat exchangers.

[0016] Compared with the prior art, the present invention has the following beneficial effects:

[0017] The dual ice slurry storage units in this experimental design operate in parallel. When the ice slurry in one unit reaches the system's set freezing rate, the other unit can replace it, enabling alternating operation of the two units. While one unit maintains system operation, the other unit discharges ice slurry and draws seawater, ensuring stable operation of the entire system. The intermediate medium transition section significantly reduces the corrosive effects of seawater on the entire system. System maintenance only requires replacing the intermediate medium transition section plates, improving the overall system's economic efficiency. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 It is a structural diagram of the utility model;

[0019] Figure 2 This is a schematic structural diagram of the supercooled water circulation section in the present utility model;

[0020] Figure 3 This is a schematic structural diagram of the intermediate medium transition section in the present utility model;

[0021] Figure 4 This is a schematic structural diagram of the steam compression cycle section of the present invention;

[0022] Figure 5 This is a structural diagram of the terminal heating cycle section in the present invention.

[0023] Reference numerals:

[0024] 1-primary filtration device, 2-first ice slurry storage device, 3-crystallization promoting device, 4-subcooling plate heat exchanger, 5-pressure gauge, 6-flow meter, 7-ice nucleus filtration device, 8-subcooling water circulation pump, 9-thermometer, 10-second ice slurry storage device, 11-ice removal pump, 12-water intake pump, 13-ethylene glycol solution replenishing device, 14-expansion tank, 15-circulation pump, 16-evaporating plate heat exchanger, 17-buffer tank, 18-compressor, 19-oil separator, 20-return oil pipe, 21-condensing plate heat exchanger, 22-liquid storage tank, 23-filtration device, 24-throttle valve, 25-heat dissipation device, 26-heating circulation pump. DETAILED DESCRIPTION

[0025] The present invention will be described in detail below with reference to the accompanying drawings and in combination with embodiments.

[0026] like Figures 1 to 5 As shown, a dual-tank seawater source ice slurry heat pump circulation system for engineering projects includes a subcooled water circulation section, an intermediate medium transition section, a steam compression circulation section, and a terminal heating circulation section. A subcooled plate heat exchanger 4 is connected between the subcooled water circulation section and the intermediate medium transition section, an evaporation plate heat exchanger 16 is connected between the intermediate medium transition section and the steam compression circulation section, and a condensation plate heat exchanger 21 is connected between the steam compression circulation section and the terminal heating circulation section.

[0027] The supercooled water circulation section includes a primary filter device 1, two ice slurry storage devices, a water intake pump 12, an ice discharge pump 11, a supercooled water circulation pump 8, an ice nucleation filter device 7 and a crystal promoting device 3. The primary filter device 1 is connected to the water intake pump 12, and each ice slurry storage device is connected to the primary filter device 1, the ice discharge pump 11 and the crystal promoting device 3 in parallel. The pipeline where seawater flows from the ice slurry storage device into the supercooled plate heat exchanger 4 is provided with a supercooled water circulation pump 8 and an ice nucleation filter device 7. The crystal promoting device 3 is provided on the pipeline where seawater flows from the supercooled plate heat exchanger 4 into the ice slurry storage device;

[0028] The intermediate medium transition section uses a 25% concentration of ethylene glycol solution as the medium. The intermediate medium transition section includes an expansion tank 14, a circulation pump 15 and a buffer tank 17. The expansion tank 14 and the circulation pump 15 are arranged on the pipeline where the medium flows from the subcooling plate heat exchanger 4 to the evaporating plate heat exchanger 16. The buffer tank 17 is arranged on the pipeline where the medium flows from the evaporating plate heat exchanger 16 to the subcooling plate heat exchanger 4.

[0029] The vapor compression cycle section includes a compressor 18, an oil separator 19, a liquid storage tank 22, a filter 23, and a throttle valve 24, wherein the compressor 18 and the oil separator 19 are arranged on the pipeline from the evaporating plate heat exchanger 16 to the condensing plate heat exchanger 21, and the liquid storage tank 22, the filter 23, and the throttle valve 24 are arranged on the pipeline from the condensing plate heat exchanger 21 to the evaporating plate heat exchanger 16;

[0030] The terminal heating cycle section is provided with a heat dissipation device 25 , and a heat circulation pump 26 is used to complete the circulation between the heat dissipation device 25 and the condensing plate heat exchanger 21 .

[0031] The dual ice slurry storage devices in parallel can realize the function of alternating operation of the dual storage devices. The ice slurry storage devices are both equipped with ice nucleation filtering devices, which can perform initial filtration of ice crystals on the seawater entering the first ice slurry storage device 2 and the second ice slurry storage device 10. The water intake pump 12 extracts an appropriate amount of treated seawater to fill the two ice slurry storage devices. The first ice slurry storage device 2 is used to maintain the operation of the unit. During operation, after the ice slurry in the first ice slurry storage device 2 reaches the freezing rate set by the system, it is switched to the second ice slurry storage device 10, and the unit continues to operate. The ice-water mixture in the first ice slurry storage device 2 is then discharged into the sea through the ice discharge pump 11, and the water intake pump 12 extracts an appropriate amount of treated seawater to replenish the first ice slurry storage device 2 for operation. The second ice slurry storage device 10 repeats the above process. When the system runs until the ice slurry in the second ice slurry storage device 10 reaches the system-set freezing rate, it switches to the first ice slurry storage device 2 and performs ice removal and water replenishment operations on the second ice slurry storage device 10 again, thereby achieving stable operation of the entire system and avoiding the shutdown of the single-tank seawater source ice slurry heat pump unit when it reaches the transportation limit, as well as the problem of pipeline blockage caused by seawater freezing. The subcooled water circulation section is equipped with a pressure gauge 5, a flow meter 6, and a thermometer 9 at both ends of the subcooled plate heat exchanger 4 to monitor the pressure, flow rate, and temperature of each pipeline.

[0032] like Figure 2As shown, the seawater operates within the subcooled water circulation section as follows: Seawater is pumped into the first ice slurry storage device 2 or the second ice slurry storage device 10 by a water intake pump 12. It undergoes initial filtration through the ice nucleation filter 7 within the ice slurry storage device. The filtered seawater circulates through the subcooled water circulation pump 8, is further filtered by the ice nucleation filter 7, and then flows into the subcooled plate heat exchanger 4, where it exchanges heat with the medium in the intermediate medium transition section. Before entering the subcooled plate heat exchanger 4, the seawater undergoes a secondary filtration by the ice nucleation filter 7 to prevent ice from forming in the subcooled plate heat exchanger 4 and clogging the pipes. When the seawater temperature is below freezing, it is in a subcooled state. The seawater flowing out of the subcooled plate heat exchanger 4 is desupercooled by the ultrasonic crystallization promoting device 3, and returns to the first ice slurry storage device 2 or the second ice slurry storage device 10 as an ice slurry, continuing the circulation.

[0033] like Figure 3 As shown, the intermediate medium transition section is provided with an ethylene glycol solution replenishing device 13. When the medium in the intermediate medium transition section is insufficient, the ethylene glycol solution replenishing device 13 is used to replenish the medium. The intermediate medium transition section begins to circulate under the action of the circulation pump 15, and circulates the medium that has absorbed heat in the subcooling plate heat exchanger 4 to the evaporating plate heat exchanger 16, transferring heat to the steam compression cycle section. The expansion tank 14 is used to balance the pressure fluctuations of the system and replenish the solution when the pressure drops due to solution loss. The buffer tank 17 is used to buffer the pressure fluctuations of the system, play the role of stabilizing pressure and unloading, and ensure the stability of the water pressure of the system. The thermometer 9 on the intermediate medium transition section is used to observe the temperature changes of the ethylene glycol solution, which is convenient for timely observation and replenishment of the ethylene glycol solution.

[0034] like Figure 4 As shown, the refrigerant in the vapor compression cycle is driven by compressor 19 through oil separator 20, then undergoes heat exchange in condensing plate heat exchanger 21, and then flows through liquid storage tank 22, filter 23, and throttle valve 24 into evaporating plate heat exchanger 16 to complete the cycle. An oil return pipe 20 is provided between the front end of compressor 18 and oil separator 19 to recover oil vapor from compressor 18 and ensure the normal operation of compressor 18's lubrication system.

[0035] like Figure 5 As shown, in the terminal heating cycle section, under the action of the heating circulation pump 26, the water that receives heat in the condensing plate heat exchanger 21 flows into the heat dissipation device 25 to release the heat, completing the cycle.

[0036] Wherein, thermometers 9 are provided on the pipelines of the supercooled water circulation section, the intermediate medium transition section and the terminal heating circulation section for observing the temperature of each pipeline.

[0037] The subcooling plate heat exchanger 4 , the evaporating plate heat exchanger 16 and the condensing plate heat exchanger 21 are all plate heat exchangers, which are used to maintain heat exchange between the four circulation sections.

[0038] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. Any modifications, equivalent replacements, improvements, etc. made within the spirit and principles of the present invention should be included in the scope of protection of the present invention.

Claims

1. A dual-tank seawater source ice slurry heat pump circulation system for engineering, characterized by: It comprises a subcooled water circulation section, an intermediate medium transition section, a steam compression circulation section and a terminal heating circulation section, wherein a subcooled plate heat exchanger (4) is connected between the subcooled water circulation section and the intermediate medium transition section, an evaporation plate heat exchanger (16) is connected between the intermediate medium transition section and the steam compression circulation section, and a condensing plate heat exchanger (21) is connected between the steam compression circulation section and the terminal heating circulation section; The supercooled water circulation section comprises a primary filtering device (1), two ice slurry storage devices, a water intake pump (12), an ice discharge pump (11) and a crystal promoting device (3); the primary filtering device (1) is connected to the water intake pump (12); each ice slurry storage device is connected to the primary filtering device (1), the ice discharge pump (11) and the crystal promoting device (3) in parallel; a supercooled water circulation pump (8) and an ice nucleation filtering device (7) are provided on a pipeline where seawater flows from the ice slurry storage device into the supercooled plate heat exchanger (4); and the crystal promoting device (3) is provided on a pipeline where seawater flows from the supercooled plate heat exchanger (4) into the ice slurry storage device; The intermediate medium transition section uses a 25% concentration of ethylene glycol solution as a medium. The intermediate medium transition section includes an expansion tank (14), a circulation pump (15) and a buffer tank (17). The expansion tank (14) and the circulation pump (15) are arranged on the pipeline where the medium flows from the subcooling plate heat exchanger (4) to the evaporating plate heat exchanger (16). The buffer tank (17) is arranged on the pipeline where the medium flows from the evaporating plate heat exchanger (16) to the subcooling plate heat exchanger (4). The steam compression cycle section comprises a compressor (18), an oil separator (19), a liquid storage tank (22), a filter device (23) and a throttle valve (24), wherein the compressor (18) and the oil separator (19) are arranged on a pipeline from the evaporating plate heat exchanger (16) to the condensing plate heat exchanger (21), and the liquid storage tank (22), the filter device (23) and the throttle valve (24) are arranged on a pipeline from the condensing plate heat exchanger (21) to the evaporating plate heat exchanger (16); The terminal heating cycle section is provided with a heat dissipation device (25), and a heat circulation pump (26) is used to complete the circulation between the heat dissipation device (25) and the condensing plate heat exchanger (21).

2. The dual-tank seawater source ice slurry heat pump circulation system for engineering according to claim 1, characterized in that: An ice nucleus filtering device (7) is provided in each of the ice slurry storage devices.

3. The dual-tank seawater source ice slurry heat pump circulation system for engineering according to claim 1, characterized in that: An ethylene glycol solution replenishing device (13) is provided in the intermediate medium transition section.

4. The dual-tank seawater source ice slurry heat pump circulation system for engineering according to claim 1, characterized in that: An oil return pipe (20) is provided between the front end of the compressor (18) and the oil separator (19).

5. The dual-tank seawater source ice slurry heat pump circulation system for engineering according to claim 1, characterized in that: Thermometers (9) are provided on the pipelines of the supercooled water circulation section, the intermediate medium transition section and the terminal heating circulation section.

6. The dual-tank seawater source ice slurry heat pump circulation system for engineering according to claim 1, characterized in that: The subcooling water circulation section is provided with a pressure gauge (5), a flow meter (6) and a thermometer (9) at both ends of the subcooling plate heat exchanger (4).

7. The dual-tank seawater source ice slurry heat pump circulation system for engineering according to claim 1, characterized in that: The subcooling plate heat exchanger (4), the evaporating plate heat exchanger (16) and the condensing plate heat exchanger (21) are all plate heat exchangers.

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