CN111023610B - Heat pump system and method for operating the same - Google Patents
Heat pump system and method for operating the same Download PDFInfo
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- CN111023610B CN111023610B CN201811180328.0A CN201811180328A CN111023610B CN 111023610 B CN111023610 B CN 111023610B CN 201811180328 A CN201811180328 A CN 201811180328A CN 111023610 B CN111023610 B CN 111023610B
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- 238000000034 method Methods 0.000 title claims description 20
- 239000007788 liquid Substances 0.000 claims abstract description 109
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims abstract description 104
- 239000002918 waste heat Substances 0.000 claims abstract description 21
- 239000007789 gas Substances 0.000 claims description 38
- 239000003507 refrigerant Substances 0.000 claims description 23
- 238000010521 absorption reaction Methods 0.000 claims description 22
- 230000006835 compression Effects 0.000 claims description 16
- 238000007906 compression Methods 0.000 claims description 16
- 239000010842 industrial wastewater Substances 0.000 claims description 15
- 238000013021 overheating Methods 0.000 claims description 11
- 238000001704 evaporation Methods 0.000 claims description 9
- 230000008020 evaporation Effects 0.000 claims description 9
- 238000009833 condensation Methods 0.000 claims description 6
- 230000005494 condensation Effects 0.000 claims description 6
- 238000005057 refrigeration Methods 0.000 claims description 4
- 238000004519 manufacturing process Methods 0.000 abstract description 9
- 238000001816 cooling Methods 0.000 abstract description 8
- 238000011084 recovery Methods 0.000 abstract description 8
- 239000002351 wastewater Substances 0.000 abstract description 8
- 238000005265 energy consumption Methods 0.000 abstract description 3
- 238000010438 heat treatment Methods 0.000 description 3
- 239000000498 cooling water Substances 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000004043 dyeing Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000009776 industrial production Methods 0.000 description 1
- 239000002440 industrial waste Substances 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- MSSNHSVIGIHOJA-UHFFFAOYSA-N pentafluoropropane Chemical compound FC(F)CC(F)(F)F MSSNHSVIGIHOJA-UHFFFAOYSA-N 0.000 description 1
- 238000007639 printing Methods 0.000 description 1
- 239000007921 spray Substances 0.000 description 1
- 238000005507 spraying Methods 0.000 description 1
- 239000010959 steel Substances 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B7/00—Compression machines, plants or systems, with cascade operation, i.e. with two or more circuits, the heat from the condenser of one circuit being absorbed by the evaporator of the next circuit
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B27/00—Machines, plants or systems, using particular sources of energy
- F25B27/02—Machines, plants or systems, using particular sources of energy using waste heat, e.g. from internal-combustion engines
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B41/00—Fluid-circulation arrangements
- F25B41/40—Fluid line arrangements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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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
- Y02A—TECHNOLOGIES FOR ADAPTATION TO CLIMATE CHANGE
- Y02A30/00—Adapting or protecting infrastructure or their operation
- Y02A30/27—Relating to heating, ventilation or air conditioning [HVAC] technologies
- Y02A30/274—Relating to heating, ventilation or air conditioning [HVAC] technologies using waste energy, e.g. from internal combustion engine
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- Engineering & Computer Science (AREA)
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- Mechanical Engineering (AREA)
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- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Drying Of Solid Materials (AREA)
- Heat-Pump Type And Storage Water Heaters (AREA)
Abstract
The invention provides a heat pump system, which comprises a low-temperature stage system and a high-temperature stage system, wherein the low-temperature stage system comprises a compressor, an evaporative condenser, an expansion valve and a first evaporator which are sequentially connected, the first evaporator is connected with an inlet of the compressor, the high-temperature stage system comprises a first steam compressor, a desuperheating heat exchanger, a first condenser, a first electronic expansion valve, a first gas-liquid separator and the evaporative condenser which are sequentially connected, and the evaporative condenser is respectively connected with an outlet of the first gas-liquid separator and an inlet of the first steam compressor. The heat pump system provided by the invention realizes waste heat recovery or water cooling of waste water at different temperatures according to different waste water temperature ranges in different industrial processes and different application requirements of heat source temperatures, and simultaneously provides medium-high temperature heat sources and compressed steam in different temperature ranges, so that the energy consumption in the industrial process is reduced, and the energy utilization efficiency is improved.
Description
Technical Field
The invention relates to the field of industrial waste heat recovery, in particular to a heat pump system and an operation method thereof.
Background
In the industrial fields of printing and dyeing, steel and the like, a large amount of high-temperature heat source steam is consumed in the industrial production process, high-temperature hot water is provided by mixing the steam and make-up water, the heating and preheating requirements in the production process are met through the heat source steam and the hot water, the utilized heat source steam and the utilized hot water are correspondingly changed into industrial wastewater in different temperature ranges, and the direct discharge of the wastewater causes huge energy loss. How to realize effective recovery according to the scope of waste water waste heat temperature, can provide the heat source of suitable temperature according to the heat supply temperature demand of different technologies such as preheating, heating simultaneously, it is crucial to improve energy utilization efficiency. In addition, except for the above-mentioned industrial waste water waste heat, the operation of a lot of industrial equipment all needs to utilize the cooling water to cool off, and the cooling water after the intensification is the cooling circulation that continues after the cooling tower cooling usually, and a large amount of waste heat is wasted to its circulation process, and industrial waste water and the water cooling heat of different temperature ranges that exist at present generally hardly have an effectual waste heat recovery method, when realizing heat recovery, can also be fine and industrial process cooperatees.
Disclosure of Invention
In view of the above, it is necessary to provide a heat pump system which can effectively realize waste heat recovery.
The invention provides a heat pump system, which comprises an evaporative condenser, a low-temperature stage system and a high-temperature stage system, wherein the evaporative condenser comprises a heat release pipeline and a heat absorption pipeline, the low-temperature stage system and the high-temperature stage system are respectively connected with the heat release pipeline and the heat absorption pipeline, the low-temperature stage system comprises a compressor, an expansion valve and a first evaporator which are sequentially connected end to end, the heat release pipeline is arranged between the compressor and the expansion valve to condense and release heat, the high-temperature stage system comprises a plurality of electromagnetic valves, a first steam compressor, a de-superheating heat exchanger, a first condenser, a first electronic expansion valve and a first gas-liquid separator which are sequentially connected end to end, the heat absorption pipeline is arranged between the first gas-liquid separator and the first steam compressor, the electromagnetic valves are arranged between the pipelines to control the flow direction of a medium, and a first electromagnetic valve is arranged between the de-superheating heat exchanger and the first condenser, the first gas-liquid separator comprises a first inlet and a first outlet, the first inlet is connected with the first electronic expansion valve, and the first outlet is connected with the inlet of the first water vapor compressor through the heat absorption pipeline.
Further, the first gas-liquid separator further comprises a second inlet and a second outlet, the second inlet is connected with a second electromagnetic valve, the second outlet is connected with the inlet of the first water vapor compressor, and a third electromagnetic valve is arranged between the second outlet and the first water vapor compressor.
Furthermore, the first outlet is connected with the evaporative condenser through a fourth electromagnetic valve, and a first one-way valve is arranged between a heat absorption pipeline of the evaporative condenser and the first water vapor compressor.
Furthermore, the high-temperature stage system also comprises a second evaporator, one end of the second evaporator is connected with a first outlet of the first gas-liquid separator through a fifth electromagnetic valve, the other end of the second evaporator is connected with an inlet of the first water vapor compressor, and a second one-way valve is arranged between the second evaporator and the first water vapor compressor.
Furthermore, the high-temperature stage system further comprises a second steam compressor, a second gas-liquid separator, a second condenser, a second expansion valve and a third gas-liquid separator which are sequentially connected, the second steam compressor is connected with the desuperheating heat exchanger through a sixth electromagnetic valve, and the third gas-liquid separator is connected with the first electronic expansion valve.
Further, the second gas-liquid separator comprises a gas outlet and a liquid outlet, the gas outlet is connected with the second condenser, a seventh electromagnetic valve is arranged between the gas outlet and the second condenser, the liquid outlet is connected with the third gas-liquid separator, and an eighth electromagnetic valve is arranged between the liquid outlet and the third gas-liquid separator.
Furthermore, the third gas-liquid separator includes a third inlet, a fourth inlet, a third outlet and a fourth outlet, the third inlet is connected to the second expansion valve, the third outlet is connected to the second steam compressor through a ninth solenoid valve, the fourth inlet is connected to the liquid outlet of the second gas-liquid separator through an eighth solenoid valve, the fourth outlet is connected to the first electronic expansion valve, and a tenth solenoid valve and a third check valve are sequentially disposed between the fourth outlet and the first electronic expansion valve.
Furthermore, the high-temperature stage system also comprises a water pump, the first gas-liquid separator is connected to the inlet of the water pump through an eleventh electromagnetic valve, and the outlet of the water pump is connected with the second steam compressor through a twelfth electromagnetic valve.
Further, the high-temperature stage system further comprises a third steam compressor, a gas outlet of the second gas-liquid separator is further connected with a thirteenth electromagnetic valve and a fourteenth electromagnetic valve respectively, and the thirteenth electromagnetic valve is connected with the third steam compressor.
The operation method of the heat pump system specifically comprises the following steps:
and 6, controlling the compressed steam in the desuperheating heat exchanger to enter a second water steam compressor through a sixth electromagnetic valve to be continuously compressed, then flowing into a second condenser through a second gas-liquid separator and a seventh electromagnetic valve to be condensed and release heat to provide a heat source, and throttling the condensed water in the second condenser through a second electronic expansion valve and then flowing into a third gas-liquid separator to perform next circulation.
The heat pump system provided by the invention realizes waste heat recovery or water cooling of waste water at different temperatures according to different waste water temperature ranges in different industrial processes and different application requirements of heat source temperatures, and simultaneously provides medium-high temperature heat sources and compressed steam in different temperature ranges, so that the energy consumption in the industrial process is reduced, and the energy utilization efficiency is improved.
Drawings
Fig. 1 is a schematic view of the overall configuration of a heat pump system according to a first embodiment of the present invention.
Fig. 2A and 2B are schematic flow charts illustrating an operation method of the heat pump system according to the first embodiment of the present invention.
Description of the main elements
The following detailed description will further illustrate the invention in conjunction with the above-described figures.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
Unless defined otherwise, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention belongs. The terminology used in the description of the invention herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. As used herein, the term "or/and" includes any and all combinations of one or more of the associated listed items.
Referring to fig. 1, fig. 1 is a schematic structural diagram of a heat pump system 100 according to an embodiment of the present invention, the heat pump system being used for recovering waste heat in industrial wastewater to provide a heat source. The heat pump system 100 includes a low temperature stage system and a high temperature stage system, and the low temperature stage system is connected to the high temperature stage system.
The low-temperature stage system comprises a compressor 1, an evaporative condenser 2, an expansion valve 3 and a first evaporator 4, wherein the evaporative condenser 2 comprises a heat release pipeline 2a and a heat absorption pipeline 2 b. The outlet of the compressor 1 is connected with a heat release pipeline 2a of the evaporative condenser 2, the heat release pipeline 2a is connected with the expansion valve 3, the expansion valve 3 is connected with the first evaporator 4, the first evaporator 4 is connected with the inlet of the compressor 1, and the heat absorption pipeline 2b is connected with the high-temperature stage system. The refrigerant absorbs heat through the first evaporator 4 and evaporates into gas, the gas enters the compressor 1, the compressed gas enters the heat release pipeline 2a for heat release, and the gas after heat release becomes liquid, and enters the first evaporator 4 after throttling and pressure reduction through the expansion valve 3, so that circulation is realized.
The high-temperature-stage system is provided with a plurality of electromagnetic valves and one-way valves, the electromagnetic valves and the one-way valves are arranged between pipelines and used for controlling the flow direction of a medium, the high-temperature-stage system comprises a first-stage compression system and a second-stage compression system, and the first-stage compression system is connected with the second-stage compression system.
The first-stage compression cycle comprises the evaporative condenser 2, a first steam compressor 5, a desuperheating heat exchanger 6, a first condenser 7, a first electronic expansion valve 8, a first gas-liquid separator 9, a second evaporator 10 and a water pump 11. The first gas-liquid separator 9 includes a first inlet 9a, a second inlet 9b, a first outlet 9c, and a second outlet 9 d. The outlet of the first water vapor compressor 5 is connected with the desuperheating heat exchanger 6, the desuperheating heat exchanger 6 is connected with the first condenser 7 through a first electromagnetic valve 12, one end of the first electronic expansion valve 8 is connected with the first condenser 7, and the other end of the first electronic expansion valve is connected with the first inlet 9a of the first gas-liquid separator 9. The second inlet 9b is connected to a second electromagnetic valve 13, and when the heat pump system 100 operates, circulating water can be added into the first gas-liquid separator 9 through the second electromagnetic valve 13, so that the balance of the circulating water of the heat pump system 100 under the high-temperature steam supply cycle is ensured. The second outlet 9d of the first gas-liquid separator 9 is connected to the inlet of the first steam compressor 5 through a third solenoid valve 14. A first outlet 9c of the first gas-liquid separator 9 is connected with a three-way pipeline, specifically, the first pipeline is connected with the second evaporator 10 through a fifth electromagnetic valve 17, and the second evaporator 10 is connected with an inlet of the first water vapor compressor 5 through a second one-way valve 18; the second pipeline is connected with a heat absorption pipeline 2b of the evaporative condenser 2 through a fourth electromagnetic valve 15, and the heat absorption pipeline 2b of the evaporative condenser 2 is connected with an inlet of the first water vapor compressor 5 through a first one-way valve 16; the third pipeline is connected with the water pump 11 through an eleventh electromagnetic valve 31, and the water pump 11 is connected with the two-stage compression system.
The two-stage compression system comprises a second steam compressor 19, a second gas-liquid separator 20, a second condenser 21, a second electronic expansion valve 22, a third gas-liquid separator 23 and a third steam compressor 24. The outlet of the desuperheating heat exchanger 6 is also connected to the inlet of the second steam compressor 19 via a sixth solenoid valve 25, the second steam compressor 19 being connected to the inlet of the second gas-liquid separator 20. The second gas-liquid separator 20 includes a gas outlet 20a and a liquid outlet 20b, the gas outlet 20a is connected to the second condenser 21, a seventh electromagnetic valve 26 is disposed between the gas outlet 20a and the second condenser 21, the liquid outlet 20b is connected to the third gas-liquid separator 23, and an eighth electromagnetic valve 27 is disposed between the liquid outlet 20b and the third gas-liquid separator 23.
The third gas-liquid separator 23 includes a third inlet 23a, a fourth inlet 23b, a third outlet 23c and a fourth outlet 23d, the second condenser 21 is connected to the second electronic expansion valve 22, the third inlet 23a is connected to the second electronic expansion valve 22, the fourth inlet 23b is connected to the liquid outlet 20b of the second gas-liquid separator 20 via the eighth solenoid valve 27, the third outlet 23c is connected to the inlet of the second water vapor compressor 19 via the ninth solenoid valve 28, and the fourth outlet 23d is connected to the first electronic expansion valve 8 via the tenth solenoid valve 29 and the third check valve 30 which are sequentially disposed. The second steam compressor 19 is connected with the water pump 11 through a twelfth electromagnetic valve 32, and the water pump 11 sprays part of water in the first gas-liquid separator 9 into the second steam compressor 19 through the eleventh electromagnetic valve 31 and the twelfth electromagnetic valve 32 to perform evaporative cooling on the compressed steam.
The third steam compressor 24 is connected to the gas outlet 20a of the second gas-liquid separator 20 through a thirteenth solenoid valve 33, the gas outlet 20a of the second gas-liquid separator 20 is also connected to the outside through a fourteenth solenoid valve 34 to supply steam to the outside, and the third steam compressor 24 is used to compress the steam to provide steam of higher temperature and pressure.
Referring to fig. 2A and 2B, fig. 2A and 2B are schematic flow charts illustrating an operation method of the heat pump system 100 according to an embodiment of the invention. The method specifically comprises the following steps:
step S1, determining the temperature of the industrial wastewater added into the heat pump system; if the temperature of the industrial wastewater is lower than 40 ℃, performing the step 2, and if the temperature of the industrial wastewater is higher than 40 ℃, performing the step 3;
step S2, recovering waste heat or absorbing heat to refrigerate and evaporate the refrigerant through a first evaporator, enabling the evaporated gaseous refrigerant to enter a compressor, compressing the gaseous refrigerant and then entering a heat release pipeline of an evaporative condenser, enabling water separated by a first gas-liquid separator to absorb heat in a heat absorption pipeline of the evaporative condenser through a fifth electromagnetic valve and evaporate into gas, enabling the gas to enter a first steam compressor through a first one-way valve to be compressed, and then eliminating overheating through a heat exchanger;
step S3, the water separated by the first gas-liquid separator enters a second evaporator through a fourth electromagnetic valve to recover waste heat for evaporation, then enters a first steam compressor through a second one-way valve to be compressed, and then is superheated through a superheating heat exchanger;
step S4, determining the temperature of a required heat source, performing step 5 if the temperature of the required heat source is between 80 and 100 ℃, performing step 6 if the temperature of the required heat source is between 100 and 130 ℃, and performing step 5 and step 6 if two heat sources of 80 to 100 ℃ and 100 to 130 ℃ are required to be provided simultaneously;
step S5, controlling the compressed steam in the desuperheating heat exchanger to enter a first condenser through a first electromagnetic valve for condensation and heat release so as to provide a heat source, and enabling condensed water to flow into a first gas-liquid separator after throttling and pressure reduction through a first electronic expansion valve so as to carry out the next cycle;
and step S6, controlling the compressed steam in the desuperheating heat exchanger to enter a second water steam compressor for continuous compression through a sixth electromagnetic valve, then flowing into a second condenser through a second gas-liquid separator and a seventh electromagnetic valve for condensation and heat release to provide a heat source, and throttling the water condensed in the second condenser through a second electronic expansion valve and then flowing into a third gas-liquid separator for next circulation.
The operation method of the heat pump system 100 specifically includes a cascade medium-temperature heat supply temperature cycle, a cascade high-temperature heat supply temperature cycle, a cascade double-heat supply temperature cycle, a single-stage medium-temperature heat supply temperature cycle, a single-stage high-temperature heat supply temperature cycle, a single-stage double-heat supply temperature cycle, and compressed steam supply, and each operation method will be further described below.
A method for operating a cascade medium-temperature heat supply temperature cycle comprises the steps of opening a first electromagnetic valve 12, a third electromagnetic valve 14 and a fourth electromagnetic valve 15, closing the rest electromagnetic valves, adding refrigerants into a low-temperature-level system, wherein the refrigerants comprise R134a, R245fa and the like, the refrigerants recover waste heat or absorb heat to refrigerate and evaporate through a first evaporator 4, the evaporated gaseous refrigerants enter a compressor 1 and enter a heat release pipeline 2a of an evaporative condenser 2 after being compressed, the condensed liquid refrigerants enter a first evaporator 4 to perform the next cycle after throttling and pressure reduction through an expansion valve 3, working medium water in the high-temperature-level system absorbs heat and evaporates into gas in a heat absorption pipeline 2b of the evaporative condenser 2, the gas enters a first water vapor compressor 5 through a first one-way valve 16 to be compressed and then is desuperheated through a desuperheating heat exchanger 6, and then flows into a first condenser 7 through the first electromagnetic valve 12 to condense and release heat, the condensed water is throttled and depressurized by the first electronic expansion valve 8 and flows into the first inlet 9a of the first gas-liquid separator 9, the separated gas flows to the inlet of the first steam compressor 5 through the second outlet 9d and the third electromagnetic valve 14, and the separated water flows into the heat absorption pipeline 2b of the evaporative condenser 2 through the first outlet 9c and the fourth electromagnetic valve 15 for the next cycle.
A cascade high-temperature heat supply temperature circulating operation method comprises the following steps of opening a third electromagnetic valve 14, a fourth electromagnetic valve 15, a sixth electromagnetic valve 25, a seventh electromagnetic valve 26, an eighth electromagnetic valve 27, a ninth electromagnetic valve 28, a tenth electromagnetic valve 29, an eleventh electromagnetic valve 31 and a twelfth electromagnetic valve 32, closing other valves, adding a refrigerant into a low-temperature system, recovering waste heat or absorbing heat for refrigeration and evaporation by the refrigerant through a first evaporator 4, enabling evaporated gaseous refrigerant to enter a compressor 1, compressing the compressed gaseous refrigerant to enter a heat release pipeline 2a of an evaporative condenser 2, throttling and depressurizing the condensed liquid refrigerant by an expansion valve 3, enabling the condensed liquid refrigerant to enter a first evaporator 4 for next circulation, enabling working medium water in the high-temperature system to absorb heat in a heat absorption pipeline 2b of the evaporative condenser 2 and evaporate into gas, enabling the gas to enter a first water vapor compressor 5 through a first one-way valve 16 for compression, and eliminating overheating through a desuperheating heat exchanger 6, then enters a second steam compressor 19 through a sixth electromagnetic valve 25 to be compressed continuously, a water pump 11 is opened, part of water separated from a first gas-liquid separator 9 is sprayed into the second steam compressor 19 through a first outlet 9c, an eleventh electromagnetic valve 31, the water pump 11 and a twelfth electromagnetic valve 32 to evaporate and cool the compressed steam, the compressed steam and the water which is not evaporated are discharged from the second steam compressor 19 and enter a second gas-liquid separator 20 to be separated, the separated steam flows into a second condenser 21 from a gas outlet 20a of the second gas-liquid separator 20 through a seventh electromagnetic valve 26 to be condensed and release heat to be used as a high-temperature heat source, the separated water flows into a third gas-liquid separator 23 through an eighth electromagnetic valve 27, the water condensed in the second condenser 21 flows into the third gas-liquid separator 23 after throttling through a second electronic expansion valve 22 to be separated, the separated steam enters an inlet of the second steam compressor through a ninth electromagnetic valve 28, the separated water flows into the first electronic expansion valve 8 through the tenth electromagnetic valve 29 and the third one-way valve 30, throttled and depressurized, and then enters the first gas-liquid separator 9, so that the next circulation is performed.
A cascade double-heat-supply temperature circulating operation method comprises the following steps that a second electromagnetic valve 13, a fifth electromagnetic valve 17, a thirteenth electromagnetic valve 33 and a fourteenth electromagnetic valve 34 are closed, the rest electromagnetic valves are opened, a refrigerant is added into a low-temperature-level system, the refrigerant recovers waste heat or absorbs heat to refrigerate and evaporate through a first evaporator 4, evaporated gaseous refrigerant enters a compressor 1 and enters a heat release pipeline 2a of an evaporative condenser 2 after being compressed, condensed liquid refrigerant enters a first evaporator 4 after throttling and pressure reduction through an expansion valve 3 to carry out the next circulation, working medium water in the high-temperature-level system absorbs heat and evaporates in a heat absorption pipeline 2b of the evaporative condenser 2 to form gas, the gas enters a first water vapor compressor 5 through a first one-way valve 16 to be compressed and then is removed of overheat through a heat exchanger 6, the gas is divided into two paths, one path of the two paths flows into a first condenser 7 through a first electromagnetic valve 12 to be condensed and released heat, providing a medium-temperature heat source, throttling and depressurizing the condensed water through a first electronic expansion valve 8, then flowing into a first inlet 9a of a first gas-liquid separator 9, circulating the separated gas to an inlet of a first water vapor compressor 5 through a second outlet 9d and a third electromagnetic valve 14, and flowing the separated water into a heat absorption pipeline 2b of the evaporative condenser 2 through a first outlet 9c and a fourth electromagnetic valve 15 for the next cycle; the other path enters the second steam compressor 19 through the sixth electromagnetic valve 25 to be compressed continuously, then is condensed by the second condenser 21 to release heat, a high-temperature heat source is provided, the condensed water in the second condenser 21 flows into the third gas-liquid separator 23 to be separated after being throttled by the second electronic expansion valve 22, the separated steam enters the inlet of the second steam compressor 19 through the ninth electromagnetic valve 28, the separated water flows into the first electronic expansion valve 8 through the tenth electromagnetic valve 29 and the third one-way valve 30 to be throttled and decompressed, and then enters the first gas-liquid separator 9, and therefore the next circulation is performed.
A single-stage medium-temperature heat supply temperature circulating operation method is characterized in that a first electromagnetic valve 12, a third electromagnetic valve 14 and a fifth electromagnetic valve 17 are opened, the rest electromagnetic valves are closed, the water flowing out of the first outlet 9c of the first gas-liquid separator 9 enters the second evaporator 10 through the fifth electromagnetic valve 17 to recover the waste heat for evaporation, then enters the first water vapor compressor 5 through the second one-way valve 18 to be compressed, then is desuperheated through the desuperheating heat exchanger 6, then flows into the first condenser 7 through the first electromagnetic valve 12 to be condensed and release heat, the condensed water is throttled and depressurized by the first electronic expansion valve 8 and flows into the first inlet 9a of the first gas-liquid separator 9, the separated gas flows to the inlet of the first steam compressor 5 through the second outlet 9d and the third electromagnetic valve 14, and the separated water enters the second evaporator 10 through the first outlet 9c and the fifth electromagnetic valve 17 to start the next cycle.
A single-stage high-temperature heat supply temperature circulating operation method comprises the steps of opening a third electromagnetic valve 14, a fifth electromagnetic valve 17, a sixth electromagnetic valve 25, a seventh electromagnetic valve 26, an eighth electromagnetic valve 27, a ninth electromagnetic valve 28, a tenth electromagnetic valve 29, an eleventh electromagnetic valve 31 and a twelfth electromagnetic valve 32, closing the rest of the electromagnetic valves, enabling water flowing out of a first outlet 9c of a first gas-liquid separator 9 to enter a second evaporator 10 through the fifth electromagnetic valve 17 to recover waste heat for evaporation, then entering a first water vapor compressor 5 through a second one-way valve 18 for compression, eliminating overheating through a superheating heat exchanger 6, then entering a second water vapor compressor 19 through the sixth electromagnetic valve 25 for continuous compression, opening a water pump 11, spraying part of water separated out of the first gas-liquid separator 9 into the second water vapor compressor 19 through the first outlet 9c, the eleventh electromagnetic valve 31, a water pump 11 and the twelfth electromagnetic valve 32 to evaporate and cool compressed steam, the compressed steam and the unevaporated water discharged from the second steam compressor 19 enter the second gas-liquid separator 20 for separation, the separated steam flows into the second condenser 21 from the gas outlet 20a of the second gas-liquid separator 20 through the seventh electromagnetic valve 26 for condensation and heat release, and is used as a high-temperature heat source, the separated water flows into the third gas-liquid separator 23 through the eighth electromagnetic valve 27, the water condensed in the second condenser 21 flows into the third gas-liquid separator 23 for separation after throttling through the second electronic expansion valve 22, the separated steam enters the inlet of the second steam compressor through the ninth electromagnetic valve 28, the separated water flows into the first electronic expansion valve 8 through the tenth electromagnetic valve 29 and the third one-way valve 30 for throttling and pressure reduction, and then enters the first gas-liquid separator 9 for next circulation.
The single-stage double-heating temperature circulating operation method specifically comprises the steps of closing the second electromagnetic valve 13, the fourth electromagnetic valve 15, the thirteenth electromagnetic valve 33 and the fourteenth electromagnetic valve 34, the other electromagnetic valves are opened, the water flowing out of the first outlet 9c of the first gas-liquid separator 9 enters the second evaporator 10 through the fifth electromagnetic valve 17 to recover the waste heat for evaporation, then enters the first water vapor compressor 5 through the second one-way valve 18 to be compressed, then is removed from overheating through the overheating heat exchanger 6, and then is divided into two paths, one path of the condensed water flows into a first condenser 7 through a first electromagnetic valve 12 for condensation and heat release to provide a medium-temperature heat source, the condensed water flows into a first inlet 9a of a first gas-liquid separator 9 after being throttled and depressurized by a first electronic expansion valve 8, the separated gas flows to an inlet of a first steam compressor 5 through a second outlet 9d and a third electromagnetic valve 14, and the separated water flows into a second evaporator 10 through a first outlet 9c and a fifth electromagnetic valve 17 for the next cycle; the other path enters a second steam compressor 19 through a sixth electromagnetic valve 25 to be compressed continuously, a water pump 11 is turned on, part of water separated from a first gas-liquid separator 9 is sprayed into the second steam compressor 19 through a first outlet 9c, an eleventh electromagnetic valve 31, the water pump 11 and a twelfth electromagnetic valve 32 to evaporate and cool the compressed steam, the compressed steam and the water which is not evaporated are discharged from the second steam compressor 19 and enter a second gas-liquid separator 20 to be separated, the separated steam flows into a second condenser 21 from a gas outlet 20a of the second gas-liquid separator 20 through a seventh electromagnetic valve 26 to condense and release heat to be used as a high-temperature heat source, the separated water flows into a third gas-liquid separator 23 through an eighth electromagnetic valve 27, the water condensed in the second condenser 21 flows into the third gas-liquid separator 23 after throttling through a second electronic expansion valve 22 to be separated, the separated steam enters an inlet of the second steam compressor through a ninth electromagnetic valve 28, the separated water flows into the first electronic expansion valve 8 through the tenth electromagnetic valve 29 and the third one-way valve 30, throttled and depressurized, and then enters the first gas-liquid separator 9, so that the next circulation is performed.
High-temperature compressed steam can be provided at the same time of all the above-mentioned circulation operations, and the compressed steam supply operation method is specifically to open the fourteenth electromagnetic valve 34, close the thirteenth electromagnetic valve 33, and the steam compressed by the second steam compressor 19 flows to the outside through the gas outlet 20a of the second gas-liquid separator 20 and the fourteenth electromagnetic valve 34; when the steam with higher temperature needs to be provided, the thirteenth electromagnetic valve 33 is opened, the fourteenth electromagnetic valve 34 is closed, and the steam compressed by the second steam compressor 19 enters the third steam compressor 24 to be compressed again to obtain the steam with higher temperature.
When the temperature of industrial wastewater in the industrial process is lower (lower than 40 ℃) or the water temperature needs to be reduced to the normal temperature or lower by a refrigeration mode, the system can operate in a overlapping mode, and a heat source is provided by an operation mode of overlapping medium-temperature heat supply temperature circulation, overlapping high-temperature heat supply temperature circulation or overlapping double-heat supply temperature circulation; when the temperature of the industrial wastewater is higher (40-80 ℃), the heat pump system can operate in a single stage, and a heat source is provided by a single-stage medium-temperature heat supply temperature cycle, a single-stage high-temperature heat supply temperature cycle or a single-stage double-heat supply temperature cycle. No matter single-stage or overlapping mode operation, corresponding heat sources can be provided according to different temperatures of the required heat sources, a medium-temperature heat source (80-100 ℃) is provided through a first-stage compression system of a high-temperature stage system, a high-temperature heat source (100-130 ℃) is provided through a second-stage compression system of the high-temperature stage system, high-temperature steam can be directly provided through a second-stage compression system of the high-temperature stage system, and the high-temperature steam can be further compressed by a third steam compressor to provide compressed steam with higher temperature to replace steam required by boiler steam.
The heat pump system provided by the invention realizes waste heat recovery or water cooling of waste water at different temperatures according to different waste water temperature ranges in different industrial processes and different application requirements of heat source temperatures, and simultaneously provides medium-high temperature heat sources and compressed steam in different temperature ranges, so that the energy consumption in the industrial process is reduced, and the energy utilization efficiency is improved.
It should be understood by those skilled in the art that the above embodiments are only for illustrating the present invention and are not to be used as a limitation of the present invention, and that suitable changes and modifications of the above embodiments are within the scope of the claimed invention as long as they are within the spirit and scope of the present invention.
Claims (3)
1. A heat pump system, characterized by: the heat pump system comprises an evaporative condenser, a low-temperature stage system and a high-temperature stage system, wherein the evaporative condenser comprises a heat release pipeline and a heat absorption pipeline, the low-temperature stage system and the high-temperature stage system are respectively connected with the heat release pipeline and the heat absorption pipeline, the low-temperature stage system comprises a compressor, an expansion valve and a first evaporator which are sequentially connected end to end, the heat release pipeline is arranged between the compressor and the expansion valve to condense and release heat, the high-temperature stage system comprises a plurality of electromagnetic valves, and a first steam compressor, a desuperheating heat exchanger, a first condenser, a first electronic expansion valve and a first gas-liquid separator which are sequentially connected end to end, the heat absorption pipeline is arranged between the first gas-liquid separator and the first steam compressor, the electromagnetic valves are arranged between the pipelines to control the flow direction of a medium, and a first electromagnetic valve is arranged between the desuperheating heat exchanger and the first condenser, the first gas-liquid separator comprises a first inlet and a first outlet, the first inlet is connected with the first electronic expansion valve, the first outlet is connected with the inlet of the first water vapor compressor through the heat absorption pipeline, the first gas-liquid separator further comprises a second inlet and a second outlet, the second inlet is connected with a second electromagnetic valve, the second outlet is connected with the inlet of the first water vapor compressor, a third electromagnetic valve is arranged between the second outlet and the first water vapor compressor, the first outlet is connected with the evaporative condenser through a fourth electromagnetic valve, a first one-way valve is arranged between the heat absorption pipeline of the evaporative condenser and the first water vapor compressor, the high-temperature stage system further comprises a second evaporator, one end of the second evaporator is connected with the first outlet of the first gas-liquid separator through a fifth electromagnetic valve, the other end of the high-temperature-stage system is connected with an inlet of the first steam compressor, a second check valve is arranged between the second evaporator and the first steam compressor, the high-temperature-stage system further comprises a second steam compressor, a second gas-liquid separator, a second condenser, a second expansion valve and a third gas-liquid separator which are sequentially connected, the second steam compressor is connected with the desuperheating heat exchanger through a sixth electromagnetic valve, the third gas-liquid separator is connected with the first electronic expansion valve, the second gas-liquid separator comprises a gas outlet and a liquid outlet, the gas outlet is connected with the second condenser, a seventh electromagnetic valve is arranged between the gas outlet and the second condenser, the liquid outlet is connected with the third gas-liquid separator, and an eighth electromagnetic valve is arranged between the liquid outlet and the third gas-liquid separator, the third gas-liquid separator comprises a third inlet, a fourth inlet, a third outlet and a fourth outlet, the third inlet is connected with the second expansion valve, the third outlet is connected with the second water vapor compressor through a ninth electromagnetic valve, the fourth inlet is connected with the liquid outlet of the second gas-liquid separator through an eighth electromagnetic valve, the fourth outlet is connected with the first electronic expansion valve, the fourth outlet is sequentially provided with a tenth electromagnetic valve and a third one-way valve between the first electronic expansion valve, the high-temperature stage system further comprises a third water vapor compressor, the gas outlet of the second gas-liquid separator is further respectively connected with a thirteenth electromagnetic valve and a fourteenth electromagnetic valve, and the thirteenth electromagnetic valve is connected with the third water vapor compressor.
2. The heat pump system of claim 1, wherein: the high-temperature stage system further comprises a water pump, the first gas-liquid separator is connected to the inlet of the water pump through an eleventh electromagnetic valve, and the outlet of the water pump is connected with the second steam compressor through a twelfth electromagnetic valve.
3. A method of operating a heat pump system according to any one of claims 1-2, characterized by: the method comprises the following steps:
step 1, determining the temperature of industrial wastewater added into a heat pump system; if the temperature of the industrial wastewater is lower than 40 ℃, performing the step 2, and if the temperature of the industrial wastewater is higher than 40 ℃, performing the step 3;
step 2, recovering waste heat or absorbing heat for refrigeration and evaporation by a first evaporator, enabling the evaporated gaseous refrigerant to enter a compressor, compressing the gaseous refrigerant and then entering a heat release pipeline of an evaporative condenser, enabling water separated by a first gas-liquid separator to absorb heat in a heat absorption pipeline of the evaporative condenser through a fifth electromagnetic valve and evaporate into gas, enabling the gas to enter a first water vapor compressor through a first one-way valve for compression, and eliminating overheating through a heat removal heat exchanger;
step 3, the water separated by the first gas-liquid separator enters a second evaporator through a fourth electromagnetic valve to recover waste heat for evaporation, then enters a first steam compressor through a second one-way valve to be compressed, and is removed from overheating through an overheating heat exchanger;
step 4, determining the temperature of a required heat source, performing step 5 if the temperature of the required heat source is between 80 and 100 ℃, performing step 6 if the temperature of the required heat source is between 100 and 130 ℃, and simultaneously performing step 5 and step 6 if two heat sources of 80 to 100 ℃ and 100 to 130 ℃ are required to be provided;
step 5, controlling the compressed steam in the desuperheating heat exchanger to enter a first condenser through a first electromagnetic valve for condensation and heat release so as to provide a heat source, and enabling condensed water to flow into a first gas-liquid separator after throttling and pressure reduction through a first electronic expansion valve so as to carry out the next cycle;
and 6, controlling the compressed steam in the desuperheating heat exchanger to enter a second water steam compressor through a sixth electromagnetic valve to be continuously compressed, then flowing into a second condenser through a second gas-liquid separator and a seventh electromagnetic valve to be condensed and release heat to provide a heat source, and throttling the condensed water in the second condenser through a second electronic expansion valve and then flowing into a third gas-liquid separator to perform next circulation.
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| CN113701387B (en) * | 2021-04-07 | 2022-10-28 | 中国科学院理化技术研究所 | Supersonic two-phase expansion multistage low-temperature refrigerating system and refrigerator |
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Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1847750A (en) * | 2005-02-28 | 2006-10-18 | 热分析股份有限责任公司 | Refrigeration device |
| CN201081401Y (en) * | 2007-01-28 | 2008-07-02 | 扬州日利达有限公司 | Low-grade waste heat recovering heat pump hot water heater |
| CN101688725A (en) * | 2007-04-24 | 2010-03-31 | 开利公司 | Transcritical refrigerant vapor compression system with charge management |
| CN103842743A (en) * | 2011-09-30 | 2014-06-04 | 大金工业株式会社 | Heat pump |
| CN103940156A (en) * | 2014-05-04 | 2014-07-23 | 江苏苏净集团有限公司 | Cascade heat pump drying system and control method thereof |
| CN104110914A (en) * | 2014-07-08 | 2014-10-22 | 北京工业大学 | Piston-type high-temperature heat pump device for waste heat recovery |
| CN104713261A (en) * | 2015-03-18 | 2015-06-17 | 沈阳一冷新能源技术有限公司 | Cascade ground source heat pump and use method thereof |
| CN205245597U (en) * | 2015-12-21 | 2016-05-18 | 苏一强 | Two compressor formula refrigerating system |
| CN206001738U (en) * | 2016-08-29 | 2017-03-08 | 上海柯茂机械有限公司 | Cascade type heat pump unit |
| CN106969523A (en) * | 2017-05-05 | 2017-07-21 | 江苏科技大学 | A kind of single-stage of selection natural refrigerant/overlapping double-standard high temperature heat pump system |
| CN207146350U (en) * | 2017-07-14 | 2018-03-27 | 刘士刚 | A kind of residual heat from boiler fume recovery system |
| CN109869937A (en) * | 2019-01-25 | 2019-06-11 | 济南大森制冷设备有限公司 | A kind of steam, Hot water units |
Family Cites Families (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7600390B2 (en) * | 2004-10-21 | 2009-10-13 | Tecumseh Products Company | Method and apparatus for control of carbon dioxide gas cooler pressure by use of a two-stage compressor |
-
2018
- 2018-10-10 CN CN201811180328.0A patent/CN111023610B/en active Active
Patent Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1847750A (en) * | 2005-02-28 | 2006-10-18 | 热分析股份有限责任公司 | Refrigeration device |
| CN201081401Y (en) * | 2007-01-28 | 2008-07-02 | 扬州日利达有限公司 | Low-grade waste heat recovering heat pump hot water heater |
| CN101688725A (en) * | 2007-04-24 | 2010-03-31 | 开利公司 | Transcritical refrigerant vapor compression system with charge management |
| CN103842743A (en) * | 2011-09-30 | 2014-06-04 | 大金工业株式会社 | Heat pump |
| CN103940156A (en) * | 2014-05-04 | 2014-07-23 | 江苏苏净集团有限公司 | Cascade heat pump drying system and control method thereof |
| CN104110914A (en) * | 2014-07-08 | 2014-10-22 | 北京工业大学 | Piston-type high-temperature heat pump device for waste heat recovery |
| CN104713261A (en) * | 2015-03-18 | 2015-06-17 | 沈阳一冷新能源技术有限公司 | Cascade ground source heat pump and use method thereof |
| CN205245597U (en) * | 2015-12-21 | 2016-05-18 | 苏一强 | Two compressor formula refrigerating system |
| CN206001738U (en) * | 2016-08-29 | 2017-03-08 | 上海柯茂机械有限公司 | Cascade type heat pump unit |
| CN106969523A (en) * | 2017-05-05 | 2017-07-21 | 江苏科技大学 | A kind of single-stage of selection natural refrigerant/overlapping double-standard high temperature heat pump system |
| CN207146350U (en) * | 2017-07-14 | 2018-03-27 | 刘士刚 | A kind of residual heat from boiler fume recovery system |
| CN109869937A (en) * | 2019-01-25 | 2019-06-11 | 济南大森制冷设备有限公司 | A kind of steam, Hot water units |
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Denomination of invention: Heat pump system and its operating methods Effective date of registration: 20230427 Granted publication date: 20211105 Pledgee: Bank of Jiangsu Co.,Ltd. Nantong Branch Pledgor: NANTONG HUAXIN CENTER AIR CONDITIONER Co.,Ltd. Registration number: Y2023980039383 |
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