CN110030763B - Operation method of gas engine driven vapor compression type air source heat pump hot and cold water unit - Google Patents

Operation method of gas engine driven vapor compression type air source heat pump hot and cold water unit Download PDF

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Publication number
CN110030763B
CN110030763B CN201910314784.8A CN201910314784A CN110030763B CN 110030763 B CN110030763 B CN 110030763B CN 201910314784 A CN201910314784 A CN 201910314784A CN 110030763 B CN110030763 B CN 110030763B
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engine
unit
cooling liquid
heat
heat exchanger
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CN110030763A (en
Inventor
加磊磊
刘凤国
张蕊
韩冰冰
刘亚军
张学换
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Lanyan High Tech Tianjin Gas Technology Co ltd
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Lanyan High Tech Tianjin Gas Technology Co ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P11/00—Component parts, details, or accessories not provided for in, or of interest apart from, groups F01P1/00 - F01P9/00
    • F01P11/02—Liquid-coolant filling, overflow, venting, or draining devices
    • F01P11/0204—Filling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P5/00—Pumping cooling-air or liquid coolants
    • F01P5/10—Pumping liquid coolant; Arrangements of coolant pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B63/00—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices
    • F02B63/06—Adaptations of engines for driving pumps, hand-held tools or electric generators; Portable combinations of engines with engine-driven devices for pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G5/00—Profiting from waste heat of combustion engines, not otherwise provided for
    • F02G5/02—Profiting from waste heat of exhaust gases
    • F02G5/04—Profiting from waste heat of exhaust gases in combination with other waste heat from 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
    • F25B13/00—Compression machines, plants or systems, with reversible cycle
    • 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
    • F25B41/30—Expansion means; Dispositions thereof
    • F25B41/31—Expansion 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
    • 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
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P7/00—Controlling of coolant flow
    • F01P7/14—Controlling of coolant flow the coolant being liquid
    • F01P2007/146—Controlling of coolant flow the coolant being liquid using valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02G—HOT GAS OR COMBUSTION-PRODUCT POSITIVE-DISPLACEMENT ENGINE PLANTS; USE OF WASTE HEAT OF COMBUSTION ENGINES; NOT OTHERWISE PROVIDED FOR
    • F02G2260/00—Recuperating heat from exhaust gases of combustion engines and heat from cooling circuits
    • 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
    • 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
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

The invention discloses a gas engine driven vapor compression type air source heat pump hot and cold water unit operation method, which comprises the following steps: the gas engine drives the compressor to do work on the refrigerant, and the flow direction of the refrigerant is switched through the four-way reversing valve, so that the refrigeration cycle and the heating cycle of the heat pump system are respectively formed; the engine cooling liquid is pumped into the smoke heat exchanger by the engine cooling liquid pump, and then enters the engine cylinder sleeve to carry the engine cylinder sleeve waste heat after absorbing the engine smoke waste heat, so that self-circulation, waste heat recovery circulation, heat dissipation circulation and defrosting circulation are respectively formed through the electric three-way valve and each electromagnetic valve according to the characteristics of the energy application occasion and the running condition of the unit. Compared with the prior art, the invention has the advantages that the waste heat of the gas engine is fully and reasonably utilized, the operation is safer and more stable, and the energy-saving effect is more obvious.

Description

Operation method of gas engine driven vapor compression type air source heat pump hot and cold water unit
Technical Field
The invention relates to a method for operating a vapor compression type air source heat pump unit, in particular to a method for operating a gas engine driven vapor compression type air source heat pump hot and cold water unit.
Background
The electric driving type air source heat pump unit utilizes the reverse circulation operation principle to extract low-grade heat energy from the atmosphere environment, converts the low-grade heat energy into high-grade heat energy, and utilizes the four-way reversing valve to switch the flow direction of the refrigerant, thereby achieving the purposes of independent refrigeration and independent heating. Therefore, compared with the traditional heat supply and domestic hot water supply modes, the electrically driven air source heat pump unit not only has higher energy efficiency, but also has more complete operation functions. In recent years, particularly under the promotion of the policy of changing coal into electricity, an electrically driven air source heat pump unit is rapidly developed. However, the running state of the electric drive type air source heat pump unit at the present stage has some defects. For example, when the air conditioner is in refrigeration operation in summer, the electric energy consumption of the electric drive type air source heat pump unit is huge, and the situation of shortage of electric power in the peak period of summer electricity consumption in China is definitely snowy frosting. Because the electrically driven air source heat pump cannot perform refrigeration and heating at the same time, the electrically driven air source heat pump unit is difficult to win for some energy-consuming places with cold and hot requirements at the same time. The defrosting problem is involved in the heating operation in winter. When the electric heating defrosting is adopted, the power consumption is larger, and the economical efficiency is poorer. When the four-way reversing valve is adopted for defrosting, heat supply is discontinuous, so that the thermal comfort of a user is affected. Therefore, the electrically driven air source heat pump unit is slightly defective in defrosting technology.
The gas engine drives the vapor compression type air source heat pump unit to input gas as energy, and the gas engine drives the compressor to do work, so that the gas engine drives the vapor compression type air source heat pump unit to have obvious technical advantages for the problems of the current stage of the electric drive type air source heat pump unit although the vapor compression type heat pump unit is completely the same as the electric drive type air source heat pump unit in the circulation principle. From the energy consumption perspective, the gas engine driven vapor compression type air source heat pump unit can adopt various fuel gases such as natural gas, petroleum gas, biogas and the like as the energy input of the unit, and can effectively solve the problems of power shortage and excessive fuel gas in summer of China. From the defrosting perspective, the gas engine driven vapor compression type air source heat pump unit can make full use of the waste heat of the engine to defrost, and the problems faced by the conventional electric drive type air source heat pump unit can be effectively avoided. The existing gas engine driven vapor compression type air source heat pump unit mainly adopts an engine cooling liquid-refrigerant heat exchanger to bear the load of an evaporator in a mode of being connected with the fin type evaporator in series or in parallel so as to solve the problem of frosting. By adopting the mode, the low-grade heat energy extracted from the atmospheric environment by the unit is reduced, and particularly when the evaporation temperature is higher than the atmospheric environment temperature due to the waste heat of the engine, the unit cannot extract heat from the low-temperature environment, so that the technical advantage that the heat pump device extracts the low-grade heat energy and converts the low-grade heat energy into high-grade heat energy is difficult to embody.
Disclosure of Invention
In order to make up the defects of the prior art, the invention provides a gas engine driven vapor compression type air source heat pump hot and cold water unit operation method. The operation method of the invention comprises the following aspects:
The gas engine drives the compressor to do work, and the low-temperature low-pressure gaseous refrigerant sucked by the air suction port of the compressor is compressed into high-temperature high-pressure gaseous refrigerant and then discharged to the oil separator through the air discharge port of the compressor. The oil separator separates the refrigerant from the refrigerant oil, the refrigerant oil enters the compressor oil return port through the oil return pipe, and the refrigerant is discharged from the outlet of the oil separator. During heating operation, gaseous refrigerant discharged from the outlet of the oil separator passes through the four-way reversing valve and then enters the plate heat exchanger (condenser). In a plate heat exchanger (condenser), a high-temperature refrigerant transfers heat to cooling water, and is condensed into a medium-temperature high-pressure liquid state. After flowing through the second one-way valve, the fifth one-way valve, the liquid storage device, the dry filter, the liquid supply electromagnetic valve, the liquid viewing mirror and the fourth one-way valve in sequence, the liquid refrigerant is expanded into a low-temperature low-pressure liquid state by virtue of the second expansion valve and the third expansion valve, and then enters the evaporator unit of the fin type heat exchanger to absorb the heat of air so as to be gasified into a low-temperature low-pressure gas state. The low-temperature low-pressure gaseous refrigerant discharged by the evaporator unit of the fin type heat exchanger flows through the four-way reversing valve and the gas-liquid separator in sequence, is sucked by the compressor from the air suction port of the compressor, and enters the next heating cycle. During refrigeration operation, the gaseous refrigerant discharged from the outlet of the oil separator passes through the four-way reversing valve and then enters the condenser unit of the fin type heat exchanger. Through the condenser unit of the fin type heat exchanger, the refrigerant transfers heat to air and is then condensed into a liquid state of medium temperature and high pressure. After passing through the seventh one-way valve and the eighth one-way valve, the liquid refrigerant sequentially flows through the sixth one-way valve, the liquid storage device, the drying filter, the liquid supply electromagnetic valve, the liquid viewing mirror and the third one-way valve, is expanded into a low-temperature low-pressure liquid state by virtue of the first expansion valve, then enters the plate heat exchanger (evaporator) to extract heat in chilled water, and is gasified into a low-temperature low-pressure gas state. The low-temperature low-pressure gaseous refrigerant sequentially flows through the four-way reversing valve and the gas-liquid separator, is sucked by the compressor from the air suction port of the compressor, and enters the next refrigeration cycle.
The engine waste heat comprises engine flue gas waste heat and cylinder sleeve waste heat. The engine cooling liquid is pumped into the smoke heat exchanger by the engine cooling liquid pump, and enters the engine cylinder sleeve after absorbing the exhaust smoke waste heat of the engine, so that the exhaust smoke waste heat of the engine cylinder sleeve is taken away. According to the environmental characteristics, energy consumption characteristics and running conditions of the unit, the opening degree of the electric three-way valve and the starting and stopping of the electromagnetic valve are controlled by a control program to adjust the flow direction and flow distribution state of the engine cooling liquid so as to meet the energy consumption requirements of the application occasions of the unit and ensure the safe and efficient running of the unit. For example, when the unit is in preheating operation, the circulation state of the engine coolant is regulated by controlling the electric three-way valve and the electromagnetic valve, so that the temperature of the engine coolant is quickly increased, and the temperature of the coolant required to be maintained for safe and efficient operation of the engine is achieved; when the unit is in refrigeration operation and the energy consumption place only has cold requirement, the circulation state of the cooling liquid of the engine is regulated by controlling the electric three-way valve and the electromagnetic valve so that the cooling liquid flows through the heat radiating unit of the fin type heat exchanger, and excessive waste heat of the engine is released into the atmosphere; when the unit is in refrigeration operation and the energy utilization place has heat utilization requirements, the circulation state of the engine cooling liquid is regulated by controlling the electric three-way valve and the electromagnetic valve, so that the cooling liquid flows through the heat recovery heat exchanger, and the engine waste heat is transmitted to a user; when the unit is in refrigeration operation and the energy consumption place has heat demand, but the heat demand is smaller, after the small heat demand of the energy consumption place is met, the cooling liquid temperature required to be maintained for ensuring the safe and efficient operation of the engine is regulated by controlling an electric three-way valve and an electromagnetic valve, so that the cooling liquid is switched from the flow direction of a heat recovery heat exchanger to the flow direction of a radiating unit of a fin type heat exchanger, excessive waste heat of the engine is transmitted to the atmosphere, and for the condition that the energy consumption place has only a small heat demand and the heat consumption is discontinuous, the flow direction of the cooling liquid between the heat recovery heat exchanger and the fin type heat exchanger radiator unit is switched by controlling the electromagnetic valve so as to achieve the aim; when the unit is in normal heating operation, the circulation mode of engine coolant is basically consistent with the circulation mode of the unit in refrigeration operation and all heat consumption requirements of an energy field, and the only difference is that the operation environments are different, so that the opening of the electric three-way valve is different; when the unit is in heating operation in a low-temperature environment and the evaporator unit is judged to be possible to frost, the circulation state of the engine cooling liquid is regulated by controlling the electric three-way valve and the electromagnetic valve, so that the cooling liquid flows through the defrosting unit of the fin type heat exchanger at regular time, and the cooling liquid is used for preheating air flowing through the fin type heat exchanger and heating fins of the evaporator unit to achieve the effect of delaying frosting; when the unit heats and operates in a low-temperature environment and the evaporator unit of the fin type heat exchanger frosts, the engine cooling liquid is preferably used for defrosting (reverse defrosting can also be adopted), the circulation state of the engine cooling liquid is regulated by controlling the electric three-way valve and the electromagnetic valve, so that the cooling liquid flows through the defrosting unit of the fin type heat exchanger, and the evaporator unit of the fin type heat exchanger is subjected to defrosting treatment.
When the cooling liquid of the engine cooling liquid system is insufficient, the engine cooling liquid water tank automatically supplements the cooling liquid to the engine cooling liquid system through the first one-way valve.
Compared with the prior art, the invention has the advantages of more remarkable energy-saving effect, higher operation stability and safety, and fully and reasonably utilizes the waste heat of the gas engine.
Drawings
Compared with the prior art, the invention has the advantages of more remarkable energy-saving effect, higher operation stability and safety, and fully and reasonably utilizes the waste heat of the gas engine.
FIG. 1 is a flow chart of a gas engine driven vapor compression type air source heat pump chiller-heater unit of the invention.
Fig. 2 is a flowchart of a first embodiment of the present invention when the unit is in cooling operation.
Fig. 3 is a flow chart of a second embodiment of the present invention during a cooling operation of the unit.
Fig. 4 is a flowchart of a first embodiment of the unit heating operation of the present invention.
Fig. 5 is a flowchart of a second embodiment of the unit heating operation of the present invention.
In the figure, 1-gas engine, 2-compressor, 3-oil separator, 4-four-way reversing valve, 5-fin heat exchanger, 6-reservoir, 7-dry filter, 8-liquid supply solenoid valve, 9-liquid view mirror, 10-first expansion valve, 11-plate heat exchanger, 12-gas-liquid separator, 13-engine coolant pump, 14-flue gas heat exchanger, 15-electric three-way valve, 16-first solenoid valve, 17-second solenoid valve, 18-third solenoid valve, 19-fourth solenoid valve, 20-heat recovery heat exchanger, 21-engine coolant tank, 22-first check valve, 23-second check valve, 24-third check valve, 25-fourth check valve, 26-fifth check valve, 27-sixth check valve, 28-seventh check valve, 29-eighth check valve, 30-second expansion valve, 31-third expansion valve
Detailed Description
The invention is described in further detail below with reference to the drawings and detailed description.
FIG. 1 is a schematic illustration of the method of the present invention for operating a gas turbine driven vapor compression air source heat pump chiller-heater unit comprising the following:
The gas engine 1 drives the compressor 2 to perform work, compresses a low-temperature low-pressure gaseous refrigerant sucked through an air suction port of the compressor 2 into a high-temperature high-pressure gaseous refrigerant, and then discharges the compressed low-temperature low-pressure gaseous refrigerant to the oil separator 3 through an air discharge port of the compressor 2. The refrigerant is separated from the refrigerant oil in the oil separator 3, the refrigerant oil enters the oil return port of the compressor 2 through the oil return pipe, and the refrigerant is discharged from the outlet of the oil separator 3. During heating operation, the gaseous refrigerant discharged from the outlet of the oil separator 3 passes through the four-way selector valve 4, and then enters the plate heat exchanger 11 (condenser), and the heat is transferred to the cooling water in the plate heat exchanger 11 (condenser), so that the refrigerant is condensed into a medium-temperature high-pressure liquid state. After flowing through the second check valve 23 and the fifth check valve 26, the liquid storage 6, the dry filter 7, the liquid supply electromagnetic valve 8, the liquid viewing mirror 9 and the fourth check valve 25 in sequence, the liquid refrigerant is expanded into a low-temperature low-pressure liquid state by virtue of the second expansion valve 30 and the third expansion valve 31, and then enters the evaporator unit 5 (b) of the fin type heat exchanger 5 (wherein 5 (b) comprises two parts of 5 (b 1) and 5 (b 2) to extract the heat of the air so as to be gasified into a low-temperature low-pressure gas state. The low-temperature low-pressure gaseous refrigerant discharged from the evaporator unit 5 (b) of the fin heat exchanger 5 flows through the four-way reversing valve 4 and the gas-liquid separator 12 in this order, is sucked by the compressor 2, and enters the next heating cycle. In the cooling operation, the gaseous refrigerant discharged from the outlet of the oil separator 3 passes through the four-way selector valve 4, then enters the condenser unit 5 (b) of the fin heat exchanger 5, and the heat is transferred to the air in the condenser unit 5 (b) of the fin heat exchanger 5, whereby the refrigerant is condensed into a medium-temperature high-pressure liquid state. After passing through the seventh check valve 28 and the eighth check valve 29, the liquid refrigerant sequentially flows through the sixth check valve 27, the liquid storage 6, the dry filter 7, the liquid supply electromagnetic valve 8, the liquid viewing mirror 9 and the third check valve 24, is expanded into a low-temperature low-pressure liquid state by virtue of the first expansion valve 10, then enters the plate heat exchanger 11 (evaporator) to absorb heat in chilled water, and is further gasified into a low-temperature low-pressure gas state. The low-temperature low-pressure gaseous refrigerant sequentially flows through the four-way reversing valve 4 and the gas-liquid separator 12 and is sucked by the compressor 2, and then enters the next refrigeration cycle.
The engine waste heat comprises engine flue gas waste heat and cylinder sleeve waste heat. The engine coolant is sent into the smoke heat exchanger 14 by the engine coolant pump 13, and after absorbing the waste heat of the engine smoke, enters the cylinder sleeve of the engine 1 to take away the waste heat of the engine cylinder sleeve. According to the environmental characteristics, energy consumption characteristics and running conditions of the unit, the opening of the electric three-way valve 15 and the starting and stopping of the electromagnetic valves 16-19 are controlled through a control program to adjust the flow direction and flow distribution state of engine cooling liquid from an engine cylinder sleeve so as to meet the energy consumption requirements of the unit application occasions and ensure the safe and efficient running of the unit. For example, when the unit is in preheating operation, the circulation state of the engine coolant is regulated by controlling the electric three-way valve 15 and the electromagnetic valves 16-19, so that the temperature of the engine coolant is quickly increased, and the temperature of the coolant required to be maintained for safe and efficient operation of the engine 1 is reached; when the unit is in refrigeration operation and the energy consumption place only has cold requirement, in order to ensure the temperature of the cooling liquid required to be maintained for safe and efficient operation of the engine 1, the circulation state of the cooling liquid of the engine is regulated by controlling the electric three-way valve 15 and the electromagnetic valves 16-19, so that the cooling liquid flows through the heat radiating unit 5 (c) of the fin type heat exchanger 5 (wherein 5 (c) comprises two parts of 5 (c 1) and 5 (c 2), and excessive waste heat of the engine is released into the atmosphere; releasing excessive waste heat of the engine into the atmosphere; when the unit is in refrigeration operation and the energy utilization place has heat utilization requirements, the circulation state of engine cooling liquid is regulated by controlling the electric three-way valve 15 and the electromagnetic valves 16-19, so that the cooling liquid flows through the heat recovery heat exchanger 20, and the engine waste heat is transmitted to a user; when the unit is in refrigeration operation and the energy consumption place has heat demand, but the heat demand is smaller, after the small heat demand of the energy consumption place is met, the cooling liquid temperature required to be maintained for ensuring the safe and efficient operation of the engine 1 is regulated by controlling the electric three-way valve 15 and the electromagnetic valves 16-19, so that the cooling liquid is switched from the flow direction of the heat recovery heat exchanger 20 to the flow direction of the heat radiating unit 5 (c) of the fin type heat exchanger 5, excessive waste heat of the engine is transmitted to the atmosphere, and the flow direction of the cooling liquid between the heat recovery heat exchanger 20 and the heat radiating unit 5 (c) of the fin type heat exchanger 5 is switched by controlling the electromagnetic valves 16-19 under the condition that the energy consumption place has only a small heat demand and the heat consumption is discontinuous so as to achieve the aim; when the unit normally heats and runs, the circulation mode of the engine coolant is basically consistent with the circulation mode of the unit when the refrigerating and running of the unit and the energy consumption place have heat consumption requirements, and the only difference is that the running environments are different, so that the opening of the electric three-way valve 15 is different; when the unit is in heating operation in a low-temperature environment and the evaporator unit 5 (b) is judged to be possible to frost, the circulation state of engine cooling liquid is regulated by controlling the electric three-way valve 15 and the electromagnetic valves 16-19, so that the cooling liquid regularly flows through the defrosting unit 5 (a) of the fin type heat exchanger 5 (wherein 5 (a) comprises two parts of 5 (a 1) and 5 (a 2)) and is used for preheating air flowing through the fin type heat exchanger 5 and heating fins of the evaporator unit 5 (b), and the effect of delaying the frosting is achieved; when the unit heats and operates in a low-temperature environment and the evaporator unit 5 (b) of the fin type heat exchanger 5 frosts, the engine cooling liquid is preferably used for defrosting (reverse defrosting can also be adopted), the circulation state of the engine cooling liquid is regulated by controlling the electric three-way valve 15 and the electromagnetic valves 16-19, so that the cooling liquid flows through the defrosting unit 5 (a) of the fin type heat exchanger 5, and the evaporator unit 5 (b) of the fin type heat exchanger 5 is subjected to defrosting treatment.
When the cooling liquid of the engine cooling liquid system is insufficient, the engine cooling liquid water tank 21 automatically supplements the cooling liquid to the engine cooling liquid system through the first check valve 22.
According to the method of operation of the present invention, it includes a heat pump refrigerant circulation system and an engine coolant circulation system.
The heat pump refrigerant circulation system comprises a gas engine 1, an output shaft of the gas engine 1 is connected with a rotating shaft of an open-type compressor 2, and an exhaust port of the compressor 2 is connected with an inlet of an oil separator 3. The oil return port of the oil separator 3 is connected with the oil return port of the compressor 2 through an oil return pipe. The outlet of the oil separator 3 is connected with an inlet pipe D of the four-way reversing valve 4, a pipe C of the four-way reversing valve 4 is connected with one end of a refrigerant channel of the plate heat exchanger 11, the other end of the refrigerant channel of the plate heat exchanger 11 is connected with the inlet end of the second one-way valve 23 and the outlet end of the first expansion valve 10, the outlet end of the second one-way valve 23, the inlet end of the first expansion valve 10, the outlet end of the third one-way valve 24 and the inlet end of the fifth one-way valve 26 are communicated, the outlet ends of the fifth one-way valve 26 and the sixth one-way valve 27 are connected with a liquid inlet pipe of the liquid accumulator 6, a liquid outlet pipe of the liquid accumulator 6 is connected with the dry filter 7, the liquid supply electromagnetic valve 8 and the liquid viewing mirror 9 in sequence, the other end of the liquid viewing mirror 9 is connected with the inlet end of the third one-way valve 24 and the inlet end of the fourth one-way valve 25, the outlet end of the fourth one-way valve 25, the inlet end of the sixth one-way valve 27, the outlet end of the seventh one-way valve 28, the outlet end of the eighth one-way valve 29, the inlet end of the second expansion valve 30 and the inlet end of the third expansion valve 31 are communicated, the inlet end of the seventh one-way valve 28 and the outlet end of the second expansion valve 30 are connected with the liquid-phase pipeline of the evaporator (condenser) unit 5 (b 1) of the fin type heat exchanger 5, the inlet end of the eighth one-way valve 29 is connected with the outlet end of the third expansion valve 31 and the liquid-phase pipeline of the evaporator (condenser) unit 5 (b 2) of the fin type heat exchanger 5, the gas-phase pipeline of the evaporator (condenser) unit 5 (b) of the fin type heat exchanger 5 is connected with the E pipe of the four-way reversing valve 4, the outlet S pipe of the four-way reversing valve 4 is connected with the inlet of the gas-liquid separator 12, and the outlet end of the gas-liquid separator 12 is connected with the air suction port of the compressor 2.
The engine cooling liquid circulation system comprises a gas engine 1, the outlet of a cylinder sleeve of the gas engine 1 is connected with an A port of an electric three-way valve 15, a B port of the electric three-way valve 15 is connected with inlet ends of a second electromagnetic valve 17, a third electromagnetic valve 18 and a fourth electromagnetic valve 19, and a C port of the electric three-way valve 15 is connected with an inlet end of a first electromagnetic valve 16. The outlet end of the second solenoid valve 17 is connected to one end of the heat recovery heat exchanger 20. The outlet end of the third electromagnetic valve 18 is connected with the inlet pipe of the defrosting unit 5 (a) of the fin type heat exchanger 5. The outlet end of the fourth electromagnetic valve 19 is connected with the inlet pipe of the heat radiating unit 5 (c) of the fin type heat exchanger 5. The outlet pipe of the defrosting unit 5 (a) of the fin heat exchanger 5, the outlet pipe of the heat radiating unit 5 (c) of the fin heat exchanger 5, the other end of the heat recovery heat exchanger 20, the outlet end of the first solenoid valve 16, and the outlet end of the first check valve 22 on the cooling liquid supplementing water pipe are communicated with the engine cooling liquid pump 13. The water supplementing port of the engine coolant water tank 21 is connected with the inlet end of the first one-way valve 22 through a coolant water supplementing pipe. The outlet of the engine coolant pump 13 is connected with one end of a cooling liquid channel of the smoke heat exchanger 14, and the other end of the cooling liquid channel of the smoke heat exchanger 14 is connected with a cooling liquid inlet of the engine 1. The exhaust outlet of the engine 1 is connected with one end of a flue gas channel of the flue gas heat exchanger 14.
The unit operation method has two embodiments during refrigeration operation.
Cooling operation first embodiment:
As shown in fig. 2, the first embodiment of the cooling operation of the unit operation method of the present invention can be used in a power use place having both cold and hot demands. In this embodiment, the gas engine 1 drives the compressor 2 to perform work, compresses a low-temperature low-pressure gaseous refrigerant sucked through the suction port of the compressor 2 into a high-temperature high-pressure gaseous state, and discharges the compressed gaseous refrigerant to the oil separator 3. The refrigerant is separated from the refrigerating oil in the oil separator 3, the refrigerating oil passes through an oil return pipe under the action of pressure difference, enters an oil return port of the compressor 2, and the refrigerant is discharged from an outlet of the oil separator 3. The gaseous refrigerant discharged from the outlet of the oil separator 3 passes through the four-way reversing valve 4 and then enters the condenser unit 5 (b) of the fin heat exchanger 5. In the condenser unit 5 (b) of the fin heat exchanger 5, the refrigerant transfers heat to air, and is condensed into a liquid state at a medium temperature and a high pressure. After passing through the seventh check valve 28 and the eighth check valve 29, the liquid refrigerant sequentially flows through the sixth check valve 27, the liquid storage 6, the dry filter 7, the liquid supply electromagnetic valve 8, the liquid viewing mirror 9 and the third check valve 24, is expanded into a low-temperature low-pressure liquid state by the first expansion valve 10, and then enters the plate heat exchanger 11 (evaporator) to absorb heat in chilled water and gasify the chilled water into a low-temperature low-pressure gas state. The low-temperature low-pressure gaseous refrigerant discharged from the plate heat exchanger 11 (evaporator) flows through the four-way reversing valve 4 and the gas-liquid separator 12 in sequence, is sucked by the compressor 2, and enters the next refrigeration cycle.
In this embodiment, the engine coolant is fed into the smoke heat exchanger 14 by the engine coolant pump 13, and after absorbing the exhaust heat of the engine, enters the cylinder liner of the engine 1, and takes away the exhaust heat of the cylinder liner of the engine. In the unit preheating operation stage, the first electromagnetic valve 16 and the second electromagnetic valve 17 are controlled to be in an open state, the third electromagnetic valve 18 and the fourth electromagnetic valve 19 are controlled to be in a closed state, and meanwhile, the opening degree of the electric three-way valve 15 is controlled to be in a fully closed state (A-B is fully closed, A-C is fully opened), so that engine cooling liquid is directly pumped into a cooling liquid channel of the flue gas heat exchanger 14 and a cylinder sleeve of the gas engine 1 after being discharged from a cylinder sleeve outlet of the gas engine 1 for cyclic heating, and the temperature of the engine cooling liquid is quickly increased to a cooling liquid temperature set value of the gas engine 1 (generally, the temperature of an engine cooling liquid inlet is set to be 70-90 ℃). After the preheating operation is finished, the opening of the electric three-way valve 15 is regulated in real time according to the heat consumption condition feedback signal of the energy consumption place and the temperature set value of the cooling liquid at the inlet of the gas engine 1, so as to meet the heat consumption requirement of the energy consumption place and ensure that the gas engine 1 always works in a safe and efficient operation environment (generally, the operation of the engine is safe and efficient when the temperature of the cooling liquid at the inlet is 70-90 ℃).
Cooling operation second embodiment:
As shown in fig. 3, the second embodiment of the cooling operation of the unit operation method of the present invention can be used for energy use sites having only a cold demand and energy use sites having a cold demand but a small heat demand. The heat pump refrigerant cycle operation mode of the second embodiment of the cooling operation is identical to the heat pump refrigerant cycle operation mode of the first embodiment of the cooling operation, and differs from the first embodiment of the cooling operation only in the engine coolant cycle operation mode. In this embodiment, the engine coolant is pumped by the engine coolant pump 13 into the flue gas heat exchanger 14, and after absorbing the exhaust heat of the engine exhaust gas, enters the cylinder liner of the engine 1 to carry away the exhaust heat of the engine cylinder liner. In the unit preheating operation stage, the first electromagnetic valve 16 and the fourth electromagnetic valve 19 are controlled to be in an open state, the second electromagnetic valve 17 and the third electromagnetic valve 18 are controlled to be in a closed state, and meanwhile, the opening degree of the electric three-way valve 15 is controlled to be in a fully closed state (A-B is fully closed, A-C is fully opened), so that engine cooling liquid is directly pumped into a cooling liquid channel of the flue gas heat exchanger 14 and a cylinder sleeve of the gas engine 1 for circulation heating after being discharged from a cylinder sleeve outlet of the gas engine 1, and the temperature of the engine cooling liquid is quickly increased to a cooling liquid temperature set value of the gas engine 1 (generally, the temperature of an engine cooling liquid inlet is set to be 70-90 ℃). After the preheating operation is finished, the engine waste heat is not required to be recovered for the energy utilization place with only refrigeration requirement, but in order to ensure safe and efficient operation of the gas engine 1, the engine waste heat is required to be discharged into the atmosphere, and the opening of the electric three-way valve 15 is regulated in real time according to the heat radiation condition feedback signal of the heat radiation unit 5 (c) of the fin type heat exchanger 5 and the temperature set value of the cooling liquid at the inlet of the gas engine 1, so as to ensure safe and efficient operation of the gas engine 1. For energy-consuming places with cold and hot demands but small heat demands, the second electromagnetic valve 17 is switched to be in an open state, the fourth electromagnetic valve 19 is closed, engine cooling liquid is switched to the heat recovery heat exchanger 20, and hot water is prepared by using the waste heat of the engine for use. After the heat consumption requirement is met, the second electromagnetic valve 17 is switched to be closed, the fourth electromagnetic valve 19 is opened, and the engine waste heat is discharged to the atmosphere through the heat radiating unit 5 (c) of the fin type heat exchanger 5. In the operation process, according to the heat exchange condition feedback signal of the heat recovery heat exchanger 20, the heat radiation condition feedback signal of the heat radiation unit 5 (c) of the fin type heat exchanger 5 and the inlet cooling liquid temperature set value of the gas engine 1, the opening degree of the electric three-way valve 15 is regulated in real time, so that the gas engine 1 always works in a safe and efficient operation environment (generally, the operation of the engine is safe and efficient when the inlet cooling liquid temperature is 70-90 ℃).
The unit operation method has two embodiments during heating operation.
Heating operation first embodiment:
As shown in fig. 4, the first embodiment of the heating operation of the unit operation method of the present invention can be used in a power-using place having a heating demand and a domestic hot water demand. In this embodiment, the gas engine 1 drives the compressor 2 to perform work, compresses a low-temperature low-pressure gaseous refrigerant sucked through the inlet of the compressor 2 into a high-temperature high-pressure gaseous state, and then discharges the compressed low-temperature low-pressure gaseous refrigerant to the oil separator 3 through the outlet of the compressor 2. The oil separator 3 separates the refrigerant from the refrigerant oil, the refrigerant oil enters an oil return port of the compressor 2 through an oil return pipe under the action of pressure difference, and the refrigerant is discharged from an outlet of the oil separator 3. The four-way reversing valve 4 is electrified during heating operation, the gaseous refrigerant discharged from the outlet of the oil separator 3 passes through the D pipe of the four-way reversing valve 4, passes through the C pipe of the four-way reversing valve 4 after passing through the four-way reversing valve 4, enters the plate heat exchanger 11 (condenser), transfers heat to cooling water in the plate heat exchanger 11 (condenser), and the refrigerant is condensed into a medium-temperature high-pressure liquid state. After flowing through the second check valve 23 and the fifth check valve 26, the liquid storage 6, the dry filter 7, the liquid supply electromagnetic valve 8, the liquid viewing mirror 9 and the fourth check valve 25 in sequence, the liquid refrigerant is expanded into a low-temperature low-pressure liquid state by virtue of the second expansion valve 30 and the third expansion valve 31, and then enters the evaporator unit 5 (b) of the fin type heat exchanger 5 to absorb the heat of the air, and is further gasified into a low-temperature low-pressure gas state. The low-temperature low-pressure gaseous refrigerant discharged from the evaporator unit 5 (b) of the fin heat exchanger 5 flows through the four-way reversing valve 4 and the gas-liquid separator 12 in this order, is sucked into the compressor 2 through the air inlet of the compressor 2, and enters the next heating cycle.
In this embodiment, the engine coolant circulation system operation mode is the same as that of the first embodiment of the cooling operation.
Heating operation of the second embodiment
As shown in fig. 5, the second embodiment of the heating operation of the unit operation method of the present invention is also referred to as a heating defrost operation embodiment, and is used for unit frosting operation and low-temperature environment frosting operation delay. The heat pump refrigerant cycle system operation mode of the second embodiment of the heating operation is identical to the heat pump refrigerant cycle system operation mode of the first embodiment of the heating operation, and differs from the first embodiment of the heating operation only in the engine coolant cycle system operation mode. The operation mode is performed by controlling the opening/closing of the second electromagnetic valve 17 and the third electromagnetic valve 18 and the opening degree of the electric three-way valve 15 on the basis of the heating operation of the first embodiment. When the ambient temperature is detected to be lower than the set value of the frosting delaying ambient temperature, the possibility of frosting is indicated when the unit operates in the operating environment, and the second electromagnetic valve 17 and the third electromagnetic valve 18 are switched in a timing start-stop mode according to the set frosting delaying time. When the second solenoid valve 17 is opened and the third solenoid valve 18 is closed, the engine coolant flows through the heat recovery heat exchanger 20, and the engine waste heat is recovered. When the second electromagnetic valve 17 is closed and the third electromagnetic valve 18 is opened, the engine coolant flows through the defrosting unit 5 (a) of the fin heat exchanger 5, and the engine waste heat is used for preheating the ambient air flowing through the fin heat exchanger 5 on the one hand and heating the fins of the evaporator unit 5 (b) of the fin heat exchanger 5 in a fin heat conduction mode on the other hand, so that the effect of delaying frosting is achieved. When it is detected that the difference between the fin tube temperature of the evaporator unit 5 (b) of the fin heat exchanger 5 and the ambient temperature reaches the defrosting set value, the third solenoid valve 18 is switched to the on state, the second solenoid valve 17 is switched to the off state, the flow of the engine coolant is switched from the heat recovery heat exchanger 20 to the defrosting unit 5 (a) of the fin heat exchanger 5, and the defrosting process is performed on the evaporator unit 5 (b). During defrosting operation, the opening of the electric three-way valve 15 is controlled in real time so as to prevent excessive defrosting and heat consumption of engine coolant in the defrosting unit 5 (a) of the fin heat exchanger 5 from causing certain damage to the operation of the gas engine 1.
The invention and its embodiments have been described above schematically, without limitation, and only a few embodiments of the invention have been shown in the drawings, without limitation to the actual structure. Therefore, if one skilled in the art is informed by the present disclosure, the modeling and connection modes of the elements are not creatively designed without departing from the gist of the invention, and the structural mode and the implementation mode similar to the technical scheme are all included in the protection scope of the present invention.

Claims (8)

1. The gas engine driven vapor compression type air source heat pump hot and cold water unit operation method is characterized by comprising a heat pump refrigerant circulation system operation method and an engine cooling liquid circulation system operation method; the operation method of the heat pump refrigerant circulation system is that a gas engine drives a compressor to do work, low-temperature low-pressure gaseous refrigerant sucked by an air suction port of the compressor is compressed into high-temperature high-pressure gas, the gas refrigerant is discharged to an oil separator through an air exhaust port of the compressor, the oil separator separates the refrigerant from refrigerating oil, the refrigerating oil enters an oil return port of the compressor through an oil return pipe, the refrigerant is discharged from an outlet of the oil separator, the gaseous refrigerant discharged from the outlet of the oil separator firstly passes through a four-way reversing valve and then enters a plate heat exchanger during heating operation, the high-temperature refrigerant transfers heat to cooling water in the plate heat exchanger and is condensed into a medium-temperature high-pressure liquid state, and the liquid refrigerant sequentially flows through a second one-way valve, The fifth one-way valve, the liquid storage device, the dry filter, the liquid supply electromagnetic valve, the liquid viewing mirror and the fourth one-way valve are expanded into a low-temperature low-pressure liquid state by virtue of the second expansion valve and the third expansion valve, then the liquid state enters the evaporator unit of the fin type heat exchanger, the heat of air is absorbed and then gasified into a low-temperature low-pressure gaseous state, the low-temperature low-pressure gaseous refrigerant discharged by the evaporator unit of the fin type heat exchanger flows through the four-way reversing valve and the gas-liquid separator in sequence, and then is sucked by the compressor from the air suction port of the compressor to enter the next heating cycle; during refrigeration operation, the gaseous refrigerant discharged from the outlet of the oil separator passes through the four-way reversing valve and then enters the condenser unit of the fin type heat exchanger, the refrigerant transfers heat to the air through the condenser unit of the fin type heat exchanger, then the air is condensed into a medium-temperature high-pressure liquid state, the liquid refrigerant sequentially passes through the sixth one-way valve, the liquid storage device, the drying filter, the liquid supply electromagnetic valve, the liquid viewing mirror and the third one-way valve after passing through the seventh one-way valve and the eighth one-way valve, is expanded into a low-temperature low-pressure liquid state by virtue of the first expansion valve, then enters the plate type heat exchanger to extract heat in the chilled water, is gasified into a low-temperature low-pressure gas state, and the low-temperature low-pressure gaseous refrigerant sequentially passes through the four-way reversing valve and the gas-liquid separator, is sucked by the compressor from the air suction port of the compressor and enters the next refrigeration cycle; the engine cooling liquid circulation system comprises a gas engine, the outlet of a cylinder sleeve of the gas engine is connected with an A port of an electric three-way valve, a B port of the electric three-way valve is connected with inlet ends of a second electromagnetic valve, a third electromagnetic valve and a fourth electromagnetic valve, and a C port of the electric three-way valve is connected with an inlet end of a first electromagnetic valve; the outlet end of the second electromagnetic valve is connected with one end of the heat recovery heat exchanger; the engine waste heat comprises engine flue gas waste heat and cylinder sleeve waste heat; the engine cooling liquid circulation system operation method is that engine cooling liquid is pumped into a flue gas heat exchanger by an engine cooling liquid pump, enters an engine cylinder sleeve after absorbing engine exhaust smoke waste heat, takes away engine cylinder sleeve waste heat, and adjusts the flow direction and flow distribution state of the engine cooling liquid from the engine cylinder sleeve by controlling the opening degree of an electric three-way valve and the start and stop of an electromagnetic valve according to the environmental characteristics, the energy consumption characteristics and the operation condition of a unit operation occasion so as to meet the energy consumption requirement of the unit application occasion and ensure the safe and efficient operation of the unit, and when the cooling liquid of the engine cooling liquid system is insufficient, an engine cooling liquid water tank automatically supplements the cooling liquid to the engine cooling liquid system through a first one-way valve.
2. The gas engine-driven vapor compression type air source heat pump hot and cold water unit operation method according to claim 1, wherein the operation method comprises the following steps: the circulation state of the engine coolant is regulated by controlling the electric three-way valve and the electromagnetic valve, so that the temperature of the engine coolant is ensured to be quickly increased when the unit is in preheating operation, and the temperature of the coolant required to be maintained when the engine is in safe and efficient operation.
3. The gas engine-driven vapor compression type air source heat pump hot and cold water unit operation method according to claim 1, wherein the operation method comprises the following steps: when the unit is in refrigeration operation and the energy utilization place only has cold requirements, the cooling liquid circulation state of the engine is regulated by controlling the electric three-way valve and the electromagnetic valve in order to ensure the cooling liquid temperature required to be maintained for safe and efficient operation of the engine, so that the cooling liquid flows through the heat dissipation unit of the fin type heat exchanger, and excessive waste heat of the engine is released into the atmosphere.
4. The gas engine-driven vapor compression type air source heat pump hot and cold water unit operation method according to claim 1, wherein the operation method comprises the following steps: when the unit is in refrigeration operation and the energy utilization place has heat utilization requirements, the circulation state of the engine cooling liquid is regulated by controlling the electric three-way valve and the electromagnetic valve, so that the cooling liquid flows through the heat recovery heat exchanger, and the engine waste heat is transmitted to a user.
5. The gas engine-driven vapor compression type air source heat pump hot and cold water unit operation method according to claim 1, wherein the operation method comprises the following steps: when the unit is in refrigeration operation and the energy consumption place has heat demand, but the heat demand is smaller, after the small heat demand of the energy consumption place is met, the cooling liquid temperature required to be maintained for ensuring the safe and efficient operation of the engine is regulated by controlling an electric three-way valve and an electromagnetic valve, so that the cooling liquid is switched from the flow direction of the heat recovery heat exchanger to the flow direction of a radiating unit of the fin type heat exchanger, excessive waste heat of the engine is transmitted to the atmosphere, and the flow direction of the cooling liquid between the heat recovery heat exchanger and the fin type heat exchanger radiator unit is switched by controlling the electromagnetic valve under the condition that the energy consumption place has only a small heat demand and the heat consumption is discontinuous, so that the purpose is achieved.
6. The gas engine-driven vapor compression type air source heat pump hot and cold water unit operation method according to claim 4, wherein the operation method comprises the following steps: when the unit normally heats and operates, the engine cooling liquid circulation mode is basically consistent with the circulation mode when the unit is in refrigeration operation and the energy consumption place has heat consumption requirements, and the only difference is that the operation environments are different, so that the opening degrees of the electric three-way valves are different.
7. The gas engine-driven vapor compression type air source heat pump hot and cold water unit operation method according to claim 3, wherein: when the unit heats and runs in a low-temperature environment and the evaporator unit is judged to be possible to frost, the circulation state of the engine cooling liquid is regulated by controlling the electric three-way valve and the electromagnetic valve, so that the cooling liquid flows through the defrosting unit of the fin type heat exchanger at regular time, and the cooling liquid is used for preheating air flowing through the fin type heat exchanger and heating fins of the evaporator unit, thereby achieving the effect of delaying frosting.
8. The gas engine-driven vapor compression type air source heat pump hot and cold water unit operation method according to claim 1, wherein the operation method comprises the following steps: when the unit heats and operates in a low-temperature environment and the evaporator unit of the fin type heat exchanger frosts, engine cooling liquid is used for defrosting, the circulation state of the engine cooling liquid is regulated by controlling an electric three-way valve and an electromagnetic valve, so that the cooling liquid flows through the defrosting unit of the fin type heat exchanger, and the evaporator unit of the fin type heat exchanger is subjected to defrosting treatment.
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