CN112815578B - A high-temperature gas heat pump system with mechanical subcooling - Google Patents
A high-temperature gas heat pump system with mechanical subcoolingInfo
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- CN112815578B CN112815578B CN202110178293.2A CN202110178293A CN112815578B CN 112815578 B CN112815578 B CN 112815578B CN 202110178293 A CN202110178293 A CN 202110178293A CN 112815578 B CN112815578 B CN 112815578B
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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
- F25B30/00—Heat pumps
- F25B30/02—Heat pumps of the compression type
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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
- F25B30/00—Heat pumps
- F25B30/06—Heat pumps characterised by the source of low potential 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
- 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
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/006—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass for preventing frost
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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
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Exhaust Gas After Treatment (AREA)
- Engine Equipment That Uses Special Cycles (AREA)
Abstract
The invention discloses a high-temperature gas heat pump system with mechanical supercooling, which comprises a heat pump subsystem, an internal combustion engine subsystem, a linkage unit and a water supply flow path, wherein the main circulation of the heat pump is formed by sequentially connecting a refrigerant channel comprising a low-temperature evaporator, a four-way reversing valve, a gas-liquid separator, a first compressor, a refrigerant channel of a first condenser, a high-temperature channel of a supercooler and a first throttle valve in series through pipelines, the mechanical supercooling sub-circulation is formed by sequentially connecting the low-temperature channel comprising the supercooler, a second compressor, a second condenser and a second throttle valve in series through pipelines, and the internal combustion engine subsystem is formed by an engine, a flue gas flow path and a cooling liquid circulation flow path. The invention has high primary energy utilization rate, can recycle the residual heat of the main cycle of the heat pump, provides higher heat supply temperature, obviously improves the uniformity of heat exchange of the system, reduces irreversible loss of heat exchange, is not easy to frost an outdoor evaporator, and obviously improves the reliability and the service life of the engine.
Description
Technical Field
The invention relates to a gas heat pump system, in particular to a high-temperature gas heat pump system with mechanical supercooling.
Background
Natural gas is an important role in energy transformation in China as a clean energy. The natural gas is steadily advanced in China, and the improvement of the energy utilization rate by adopting the high-efficiency energy-saving technology is vital to the application and development of the natural gas.
The gas heat pump integrates two mature technologies of an engine and a vapor compression type circulating device, so that the development space and market requirements of the gas technology are greatly expanded. The gas heat pump utilizes the gas engine to drive the compressor to pump heat from a low-temperature heat source to a high-temperature heat source, is an efficient and energy-saving device for improving the utilization rate of primary energy, and meanwhile, the waste heat generated by the gas internal combustion engine can be further used for heat supply, so that the heat energy conversion efficiency is high.
For industrial processes with heat supply requirements exceeding 80 ℃, the conventional heat pump systems on the market at present need to adopt high-cost special high-temperature compressors, and heat pumps such as carbon dioxide and the like are not marketized on a large scale due to the difficulties of high-pressure control, high cost and the like. In contrast, the engine waste heat of the gas heat pump belongs to a high-temperature waste heat range, and if the waste heat is directly used for heating heat exchange fluid, high-temperature or ultrahigh-temperature heat supply can be further realized. Therefore, in high temperature industrial processes, gas heat pumps have significant technical and cost advantages.
However, due to the characteristics of application scenes such as drying, the heat exchange fluid is usually in a circulating heating mode, and the temperature of the heat exchange fluid entering the gas heat pump is also higher. Thus, while the condensing temperature of a gas heat pump may be lower than the heating temperature, the higher inlet fluid temperature may cause it to reach about 60 ℃. The existing gas heat pump system generally adopts a single engine to drive a single compressor mode, and for the single-stage heat pump system, the excessive valve front temperature can cause obvious throttling loss, and the energy efficiency of the system is reduced, so that the primary energy utilization efficiency of the gas heat pump is reduced. Meanwhile, for the application scene with larger temperature difference of the supplied and returned water, the uniformity of the temperature difference field can not be well ensured due to the two-stage heat supply of the heat pump and the waste heat of the engine, so that larger irreversible heat exchange loss is caused.
On the other hand, the problem of frosting at low temperature of the air source heat pump is also an important difficulty affecting the performance of the unit. When the electric drive heat pump operates in winter, defrosting is needed in time, extra power is consumed, and the heating effect is influenced. Generally, defrosting is needed once every 30-120 minutes, and the electricity consumption is increased by 10%.
Disclosure of Invention
In order to meet the heat supply requirement of a high-temperature industrial process, improve the energy utilization efficiency of a gas heat pump unit and improve the frosting condition of an air source heat pump, the invention provides a high-temperature gas heat pump system with mechanical supercooling.
The aim of the invention can be achieved by the following technical scheme:
The high-temperature gas heat pump system with the mechanical supercooling is characterized by comprising a heat pump subsystem, an internal combustion engine subsystem, a linkage unit and a water supply flow path;
The heat pump subsystem consists of a heat pump main cycle and a mechanical supercooling sub cycle, wherein the heat pump main cycle consists of a refrigerant channel comprising a low-temperature evaporator, a four-way reversing valve, a gas-liquid separator, a first compressor, a refrigerant channel of a first condenser, a high-temperature channel of a supercooler and a first throttle valve which are sequentially connected in series through pipelines, and the first throttle valve is connected with the refrigerant channel of the low-temperature evaporator again to form a cycle;
The internal combustion engine subsystem consists of an engine, a smoke flow path and a cooling liquid circulation flow path, wherein the smoke flow path consists of an exhaust pipe of the engine, a smoke passage of a three-way catalyst, a smoke passage of a first smoke heat exchanger, a smoke passage of a second smoke heat exchanger and a smoke passage of the low-temperature evaporator which are sequentially connected in series through pipelines, and low-temperature smoke is finally discharged from the low-temperature evaporator;
The linkage unit consists of a first electromagnetic clutch, a second electromagnetic clutch, a first belt pulley and a second belt pulley, wherein the first electromagnetic clutch is connected with an input shaft of the first compressor and is connected with an output shaft of the engine through the first belt pulley;
The water supply flow path is formed by sequentially connecting a heat storage water tank, a water pump, a secondary refrigerant channel of the first condenser, a secondary refrigerant channel of the second condenser, a secondary refrigerant channel of the cooling liquid heat exchanger and a secondary refrigerant channel of the second flue gas heat exchanger in series through pipelines, and then returning to the heat storage water tank.
The liquid refrigerant of the heat pump main cycle and the mechanical subcooling sub-cycle may be conventional synthetic refrigerants such as R410A, R134a, R1234yf, etc., or natural refrigerants such as R744 (CO 2). If the refrigerant is R744, the working modes of the heat pump main cycle and the mechanical supercooling sub-cycle are both transcritical cycles, the exothermic process has temperature slippage, and the mechanical supercooling sub-cycle has more remarkable energy efficiency improvement for the heat pump system.
Further, the low-temperature evaporator is a refrigerant-air/flue gas heat exchanger, is provided with a refrigerant channel and an air/flue gas channel, and is commonly a finned tube heat exchanger. The subcooler is a refrigerant-refrigerant heat exchanger and is provided with double refrigerant channels, common types are a plate heat exchanger, a double-pipe heat exchanger and the like, a high-temperature channel inlet of the subcooler is connected with an exhaust port of the main circulation compressor through a pipeline, a high-temperature channel outlet of the subcooler is communicated with the first throttle valve through a pipeline, a low-temperature channel inlet of the subcooler is communicated with the second throttle valve through a pipeline, and a low-temperature channel outlet of the subcooler is communicated with an air suction port of the sub-circulation compressor through a pipeline.
Further, the first condenser and the second condenser are refrigerant-to-coolant heat exchangers having refrigerant channels and coolant channels, commonly referred to as plate heat exchangers, double-pipe heat exchangers, and the like. The first throttle valve and the second throttle valve are common throttle devices such as an electronic expansion valve and the like and are used for adjusting the flow of the refrigerant by controlling the superheat degree of an outlet.
Further, the three-way catalyst is provided with a flue gas channel and a secondary refrigerant channel, wherein the flue gas channel is connected with an exhaust pipe of the engine, harmful gas is converted into harmless carbon dioxide, water and nitrogen through oxidation and reduction, and the secondary refrigerant channel is used for cooling liquid flowing heat exchange. The first flue gas heat exchanger and the second flue gas heat exchanger are coolant-flue gas heat exchangers and are provided with coolant channels and flue gas channels, and the common type can be a double-pipe heat exchanger, a plate heat exchanger and the like due to smaller flue gas flow. The cooling liquid heat exchanger is a refrigerant-secondary refrigerant heat exchanger and is provided with double secondary refrigerant channels, and common types are a plate heat exchanger, a sleeve heat exchanger and the like.
In one embodiment of the invention, the first compressor is a vapor-supplementing enthalpy-increasing compressor and is provided with an air suction port, an air exhaust port and a vapor supplementing port, at this time, a flash tank is arranged in the main cycle of the heat pump and is used for separating liquid refrigerant and gaseous refrigerant after one-time throttling, the flash tank is provided with a liquid inlet, a liquid outlet and an air outlet, the first throttle valve is firstly connected with the liquid inlet of the flash tank, the liquid outlet of the flash tank is connected with the inlet of a third throttle valve, the outlet of the third throttle valve is connected with a refrigerant channel of the low-temperature evaporator, and the air outlet of the flash tank is connected with the vapor supplementing port of the first compressor.
The working process of the high-temperature gas heat pump system comprises the steps that gas is combusted in an engine and outputs mechanical work, and a first compressor and a second compressor are driven by a belt pulley and an electromagnetic clutch to drive the heat pump system to work; in the main circulation of the heat pump, a low-temperature low-pressure liquid refrigerant absorbs heat and is vaporized in a low-temperature evaporator to absorb low-grade heat energy of ambient air, then the low-temperature low-pressure liquid refrigerant enters a gas-liquid separator through a four-way reversing valve, refrigerant gas is compressed into high-temperature high-pressure gas through a first compressor, the high-temperature high-pressure gas heats backwater in a first condenser, is further cooled by a mechanical supercooling subcycle through a supercooler, is changed into low-temperature low-pressure liquid through a first throttle valve and is re-entered into the low-temperature evaporator for the next circulation, in the mechanical supercooling subcycle, the low-temperature low-pressure liquid refrigerant is evaporated and absorbs heat in the supercooler to recover heat of the high-temperature refrigerant of the main circulation of the heat pump, the backwater is compressed into high-temperature high-pressure gas through a second compressor, the backwater is heated in the second condenser, and finally the backwater is changed into low-temperature low-pressure liquid refrigerant through a second throttle valve to be re-entered into the supercooler for the next circulation.
The working process of the flue gas flow path is that high-temperature flue gas discharged by an exhaust pipe of the engine firstly enters a flue gas channel of the three-way catalyst, is catalytically converted into harmless carbon dioxide, water and nitrogen, exchanges heat with cooling liquid, firstly enters the flue gas channel of the first flue gas heat exchanger to exchange heat with the cooling liquid, secondly enters the flue gas channel of the second flue gas heat exchanger to exchange heat with backwater, finally enters a flue gas channel of the low-temperature evaporator, improves the evaporation temperature of the low-temperature evaporator, prevents coil frosting, and finally is discharged from the low-temperature evaporator.
The working process of the cooling liquid circulation loop is that low-temperature cooling liquid enters the cylinder sleeve to exchange heat and cool the engine, then the cooling liquid sequentially passes through the secondary refrigerant channel of the three-way catalyst and the secondary refrigerant channel of the first smoke heat exchanger to absorb the waste heat of high-temperature smoke, then the cooling liquid is sent into the high-temperature channel of the cooling liquid heat exchanger through the cooling liquid circulation pump to exchange heat and cool with backwater from the second condenser, and then the cooling liquid enters the cylinder sleeve again to perform the next circulation.
The working process of the water supply flow path is that backwater is firstly introduced into the heat storage water tank, then enters the secondary refrigerant channel of the first condenser through the water pump, is heated by the primary circulation of the heat pump, then enters the secondary refrigerant channel of the second condenser, is heated by the secondary circulation of the mechanical supercooling particles, is then introduced into the secondary refrigerant channel of the cooling liquid heat exchanger and the secondary refrigerant channel of the second flue gas heat exchanger, is continuously heated to the heat supply temperature, and finally enters the heat storage water tank for supplying.
The high-temperature gas heat pump system has defrosting requirements when operated for a long time under extreme working conditions. And in the defrosting mode, the mechanical supercooling subcycle stops working, and the working process of the main cycle of the heat pump is that high-temperature and high-pressure gas discharged from the first compressor enters the low-temperature evaporator through the four-way reversing valve to be condensed and released heat, the coil pipe is defrosted, the high-pressure gas is changed into low-temperature and low-pressure liquid through the second throttle valve, then enters the first condenser to be evaporated and absorbed, and finally enters the first compressor again through the four-way reversing valve to be compressed again into high-temperature and high-pressure gas for next cycle.
The invention is characterized in that:
the method comprises the steps of (1) heating by adopting a gas engine to drive a heat pump system to generate high-temperature hot water suitable for industrial drying, (2) overlapping mechanical supercooling subcycles at an outlet of a main cycle condenser to recover residual heat of the main cycle condenser and provide higher heating temperature, 3) improving the temperature of the hot water by adopting a step heating mode according to different heating temperature levels of waste heat of the heat pump unit and the gas engine based on a temperature field uniformity matching principle, (4) driving two compressors by adopting a single gas engine, and (5) introducing low-temperature flue gas (50-70 ℃) subjected to heat recovery into an outdoor evaporating coil to prevent frosting.
Compared with the prior art, the invention has the beneficial effects that:
The invention adopts an internal combustion engine to drive a heat pump to absorb environmental heat, and simultaneously recovers high-temperature waste heat of the engine, reduces the condensation temperature of the heat pump, has high primary energy utilization rate and high water supply temperature, adopts a mechanical supercooling subsystem to recover the residual heat of the main cycle of the heat pump, reduces throttling loss, further heats hot water coming out of the main cycle, provides higher heat supply temperature, further improves the energy efficiency of the heat pump system, reduces the condensation temperature of the main cycle compared with a single machine system, obviously improves the heat exchange uniformity of the system, reduces irreversible heat exchange loss, obviously improves the energy efficiency of the electric drive heat pump under the same heat supply temperature, has the same capacity adjustment characteristic, has the same rotating speed adjustment trend, has good load operation characteristic, can realize stable and high-precision energy adjustment, is difficult to frost an outdoor evaporator, obviously delays frost blockage by utilizing low-temperature flue gas and the waste heat of the engine, ensures normal operation under the extremely low environmental temperature (-20 ℃) condition, simultaneously has reduced start times of the engine, obviously improves the reliability and the service life of the engine, can not influence the continuous drying process of the waste heat of the engine, and can not ensure the heat of the heat storage tank.
Drawings
FIG. 1 is a schematic flow chart of a high temperature heating mode in embodiment 1 of the present invention;
FIG. 2 is a flow chart of the defrosting mode of embodiment 1 of the present invention;
FIG. 3 is a schematic flow chart of a high temperature heating mode in embodiment 2 of the present invention;
FIG. 4 is a schematic flow chart of a high temperature heating mode in embodiment 3 of the present invention;
In the figure, the low-temperature evaporator, the 2-four-way reversing valve (4 channels are respectively 2A, 2B, 2C and 2D), the 3-gas-liquid separator, the 4-first compressor (4A-air suction port, 4B-air exhaust port and 4C-air supplementing port), the 5-first condenser, the 6-subcooler, the 7-second compressor (7A is the air suction port and 7B is the air exhaust port), the 8-second condenser, the 9-second throttle valve, the 10-first throttle valve, the 11-engine, the 12-cylinder sleeve, the 13-three-way catalyst, the 14-first flue gas heat exchanger, the 15-second flue gas heat exchanger, the 16-cooling liquid heat exchanger, the 17-cooling liquid circulating pump, the 18-water pump, the 19-heat storage water tank, the 20-first electromagnetic clutch, the 21-second electromagnetic clutch, the 22-first belt pulley, the 23-second belt pulley, the 24-flash tank and the 25-third throttle valve are arranged.
Detailed Description
The invention will now be described in detail with reference to the drawings and specific examples.
Example 1
A high temperature gas heat pump system with mechanical supercooling comprises a heat pump subsystem, an internal combustion engine subsystem, a linkage unit and a water supply flow path, and the structure is shown in figure 1.
The heat pump subsystem consists of a heat pump main cycle and a mechanical supercooling sub-cycle, wherein the heat pump main cycle consists of a refrigerant channel comprising a low-temperature evaporator 1, a four-way reversing valve 2, a gas-liquid separator 3, a first compressor 4, a refrigerant channel of a first condenser 5, a high-temperature channel of a supercooler 6 and a first throttle valve 10 which are sequentially connected in series through pipelines, the first throttle valve 10 is connected with the refrigerant channel of the low-temperature evaporator 1 again to form a cycle, the supercooler 6 is arranged at an outlet of the first condenser 5 and used for further condensation and supercooling of the refrigerant, and the mechanical supercooling sub-cycle consists of the low-temperature channel comprising the supercooler 6, a second compressor 7, a second condenser 8 and a second throttle valve 9 which are sequentially connected in series through pipelines, and the second throttle valve 9 is connected with the low-temperature channel of the supercooler 6 again to form a cycle;
The internal combustion engine subsystem consists of an engine 11, a flue gas flow path and a cooling liquid circulation flow path, wherein the flue gas flow path consists of an exhaust pipe of the engine 11, a flue gas passage of a three-way catalyst 13, a flue gas passage of a first flue gas heat exchanger 14, a flue gas passage of a second flue gas heat exchanger 15 and a flue gas passage of the low-temperature evaporator 1 which are sequentially connected in series through pipelines, the cooling liquid circulation flow path consists of a high-temperature passage of a cooling liquid heat exchanger 16, a cylinder sleeve 12, a secondary refrigerant passage of the three-way catalyst 13, a secondary refrigerant passage of the first flue gas heat exchanger 14 and a cooling liquid circulation pump 17 which are sequentially connected in series through pipelines, the cooling liquid circulation pump 17 is connected with the high-temperature passage of the cooling liquid heat exchanger 16 again to form circulation, the cylinder sleeve 12 is a cylindrical part arranged in a cylinder block hole of the engine 11 and is tightly fixed on the cylinder cover, and a piston reciprocates in an inner hole of the cylinder cover and is cooled by cooling water;
The linkage unit consists of a first electromagnetic clutch 20, a second electromagnetic clutch 21, a first belt pulley 22 and a second belt pulley 23, wherein the first electromagnetic clutch 20 is connected with an input shaft of the first compressor 4 and is connected with an output shaft of the engine 11 through the first belt pulley 22, the second electromagnetic clutch 21 is connected with an input shaft of the second compressor 7 and is connected with an output shaft of the engine 11 through the second belt pulley 23, and the engine 11 drives the first compressor 4 and the second compressor 7 through the belt pulleys and the electromagnetic clutch;
The water supply flow path is formed by sequentially connecting a heat storage water tank 19, a water pump 18, a secondary refrigerant channel of the first condenser 5, a secondary refrigerant channel of the second condenser 8, a secondary refrigerant channel of the cooling liquid heat exchanger 16 and a secondary refrigerant channel of the second flue gas heat exchanger 15 in series through pipelines, and then returning to the heat storage water tank 19.
Further, the low-temperature evaporator 1 is a fin-tube heat exchanger, and is provided with a refrigerant passage and an air/flue gas passage.
Further, the subcooler 6 is a double pipe heat exchanger, and has a double refrigerant passage.
Further, the first condenser 5 and the second condenser 8 are refrigerant-to-coolant heat exchangers having refrigerant channels and coolant channels, and are commonly known as plate heat exchangers, double pipe heat exchangers, and the like.
Further, the first throttle valve 10 and the second throttle valve 9 are electronic expansion valves for adjusting the flow rate of the refrigerant by controlling the degree of superheat of the outlet.
Further, the three-way catalyst 13 has a flue gas passage connected to an exhaust pipe of the engine, and a coolant passage for coolant flowing heat exchange, which converts harmful gases into harmless carbon dioxide, water and nitrogen by oxidation and reduction.
Further, the first flue gas heat exchanger 14 and the second flue gas heat exchanger 15 are coolant-flue gas heat exchangers, and are provided with coolant channels and flue gas channels, and the common type can be a double-pipe heat exchanger, a plate heat exchanger and the like due to smaller flue gas flow.
Further, the coolant heat exchanger 16 is a refrigerant-coolant heat exchanger, and is provided with dual coolant channels, and is commonly referred to as a plate heat exchanger, a double pipe heat exchanger, or the like.
The high temperature gas heat pump system with mechanical supercooling of embodiment 1 has two modes of high temperature heat supply and defrosting, and the detailed workflow is as follows:
1. In the high-temperature heat supply mode, as shown in fig. 1, a channel 2A of the four-way reversing valve 2 is communicated with a channel 2D, and a channel 2B is communicated with a channel 2C;
The working process of the linkage unit is that the fuel gas burns in the engine 11 and outputs mechanical work, the first compressor 4 is driven by the first belt pulley 22 and the first electromagnetic clutch 20, the second compressor 7 is driven by the second belt pulley 23 and the second electromagnetic clutch 21, and the first compressor 4 and the second compressor 7 drive the heat pump subsystem to work.
The working process of the heat pump system comprises the steps that in the main circulation of the heat pump, low-temperature low-pressure liquid refrigerant absorbs heat and evaporates in a low-temperature evaporator 1, low-grade heat energy of ambient air is absorbed, the low-temperature low-pressure liquid refrigerant enters a gas-liquid separator 3 through a four-way reversing valve 2 to separate unvaporized liquid, the liquid is prevented from being absorbed by a compressor, the refrigerant gas enters a first compressor 4 to be compressed into high-temperature high-pressure gas, the high-temperature high-pressure gas heats backwater in the first condenser 5, the backwater is further cooled by a mechanical supercooling sub-circulation through a supercooler 6, and finally the low-temperature low-pressure liquid refrigerant is changed into low-temperature low-pressure liquid refrigerant through a first throttle valve 10 to be re-entered into the low-temperature evaporator 1 for the next circulation, in the mechanical supercooling sub-circulation, the low-temperature low-pressure liquid refrigerant absorbs heat and evaporates in the supercooling sub-circulation 6, heat of high-temperature refrigerant fluid in the main circulation of the heat pump is recovered, the backwater is compressed into high-temperature high-pressure gas through a second compressor 7, the backwater is heated in the second condenser 8, and finally the low-temperature low-pressure liquid refrigerant is changed into low-temperature low-pressure liquid refrigerant through a second throttle valve 9, and the low-temperature low-pressure liquid refrigerant is re-entering the supercooling sub-circulation 6 for the next circulation.
The working process of the water supply flow path is that backwater is firstly introduced into the heat storage water tank 19, then enters the secondary refrigerant channel of the first condenser 5 through the water pump 18, is heated by the primary circulation of the heat pump, then enters the secondary refrigerant channel of the second condenser 8, is heated by the secondary circulation of the mechanical supercooler, is then sent into the secondary refrigerant channel of the cooling liquid heat exchanger 16 and the secondary refrigerant channel of the second flue gas heat exchanger 15, is heated to the heat supply temperature by the three-stage heating and the four-stage heating, and finally enters the heat storage water tank 23 for supplying.
The working process of the flue gas flow path is that the high-temperature flue gas discharged by the exhaust pipe of the engine 11 firstly enters a flue gas channel of the three-way catalyst 13, is catalytically converted into harmless carbon dioxide, water and nitrogen, exchanges heat with cooling liquid, firstly enters the flue gas channel of the first flue gas heat exchanger 14 to exchange heat with the cooling liquid, then enters a flue gas channel of the second flue gas heat exchanger 15 to further heat backwater, finally enters a flue gas channel of the low-temperature evaporator 1, improves the evaporation temperature of the low-temperature evaporator 1, prevents coil frosting, and finally is discharged from the low-temperature evaporator 1.
The working process of the cooling liquid circulation loop is that low-temperature cooling liquid enters the cylinder sleeve 12 to exchange heat and cool the engine 11, then passes through the secondary refrigerant channel of the three-way catalyst 13 and the secondary refrigerant channel of the first flue gas heat exchanger 14 in sequence to absorb the residual heat of high-temperature flue gas, at the moment, the temperature of the cooling liquid is increased, and then is sent into the high-temperature channel of the cooling liquid heat exchanger 16 through the cooling liquid circulation pump 17 to exchange heat and cool with backwater from the second condenser 8, and then enters the cylinder sleeve 12 again to carry out the next circulation.
2. Defrosting mode
In the invention, the residual heat of low-temperature flue gas of the engine is utilized to obviously delay the frost blockage of the coil pipe of the low-temperature evaporator 1, but when the engine runs for a long time under extreme working conditions, the unit still has defrosting requirements. As shown in fig. 2, in the defrosting mode, the four-way reversing valve 2A of the heat pump main cycle is communicated with 2B, and 2C is communicated with 2D;
The working process of the heat pump main cycle is that high-temperature high-pressure gas discharged from the first compressor 4 enters the low-temperature evaporator 1 through the four-way reversing valve 2 to condense and release heat, a coil pipe of the low-temperature evaporator 1 is defrosted, the high-pressure gas is changed into low-temperature low-pressure liquid through the second throttle valve 10, then enters the first condenser 5 to evaporate and absorb heat, absorbs heat of backwater, finally enters the first compressor 4 again through the four-way reversing valve 2, and is recompressed into high-temperature high-pressure gas to be circulated next time.
In the defrosting mode, the mechanical supercooling sub-cycle stops working, and the working process of the internal combustion engine subsystem is the same as that of the high-temperature heat supply mode.
The working process of the water supply flow path is that backwater is sent into a secondary refrigerant channel of the first condenser 5 through a water pump 18 to provide defrosting heat for the heat pump system, then is sequentially sent into the cooling liquid heat exchanger 16 and the second flue gas heat exchanger 15 to be heated again, and finally is sent back to the heat storage water tank 19. Therefore, in the defrosting mode, the heat pump system finally absorbs the waste heat of the internal combustion engine to defrost, the hot water bears the heat transport function, and the water temperature in the heat storage water tank is not affected.
Example 2
A high temperature gas heat pump system with mechanical supercooling comprises a heat pump subsystem, an internal combustion engine subsystem, a linkage unit and a water supply flow path, and the structure is shown in figure 3.
Compared with the embodiment 1, the first compressor 4 in the embodiment 2 is a vapor-supplementing enthalpy-increasing compressor, and has a vapor supplementing port 4C in addition to the vapor intake port 4A and the vapor exhaust port 4B, and at this time, a flash tank 24 is disposed in the main cycle of the heat pump, for separating the liquid refrigerant from the gaseous refrigerant after one throttling, the flash tank 24 has a liquid inlet, a liquid outlet and a gas outlet, the first throttle valve 10 is first connected to the liquid inlet of the flash tank 24, the liquid outlet of the flash tank 24 is connected to the inlet of a third throttle valve 25, the outlet of the third throttle valve 25 is connected to the refrigerant channel of the low-temperature evaporator 1, and the gas outlet of the flash tank 24 is connected to the vapor supplementing port of the first compressor 4. The first throttle valve 10 throttles the refrigerant once, the throttled refrigerant enters the flash tank 24, the third throttle valve 25 is used for secondarily throttling the liquid refrigerant separated from the flash tank 24, and the first compressor 4 adopts a gas-supplementing enthalpy-increasing compressor to realize two-stage compression, so that the pressure ratio is reduced, and the energy efficiency of the heat pump system is improved.
Example 2 can also realize two modes of high temperature heat supply and defrosting, and the principle is the same as that of example 1.
It should be noted that in example 2, the air make-up enthalpy is not limited to be achieved by adding the flash tank 24, but can also be achieved by adding an economizer.
Example 3
A high temperature gas heat pump system with mechanical supercooling comprises a heat pump subsystem, an internal combustion engine subsystem, a linkage unit and a water supply flow path, and the structure is shown in figure 4.
Compared with the embodiment 1, the heat pump subsystem is kept unchanged, and the heat supply temperature can be further increased by utilizing the high-temperature flue gas of the engine because the engine waste heat belongs to the high-temperature waste heat range.
The internal combustion engine subsystem is provided with a second flue gas heat exchanger 15, and consists of the engine 11, a flue gas flow path and a cooling liquid circulation flow path;
the flue gas flow path comprises an exhaust pipe of the engine 11, a flue gas channel of the three-way catalyst 13, a flue gas channel of the first flue gas heat exchanger 14 and a flue gas channel of the low-temperature evaporator 1 which are sequentially connected in series;
the cooling liquid circulation flow path comprises a high-temperature channel of the cooling liquid heat exchanger 16, the cylinder sleeve 12 and the cooling liquid circulation pump 17 which are sequentially connected in series, and the cooling liquid circulation pump 17 is connected with the high-temperature channel of the cooling liquid heat exchanger 16 again to form circulation;
The water supply flow path comprises the heat storage water tank 19, the water pump 18, the secondary refrigerant channel of the first condenser 5, the secondary refrigerant channel of the second condenser 8 and the secondary refrigerant channel of the cooling liquid heat exchanger 16 which are sequentially connected in series, and then sequentially connected with the secondary refrigerant channel of the flue gas heat exchanger 14 and the secondary refrigerant channel of the three-way catalyst 13, and is further heated to ultra-high temperature by high-temperature flue gas, and finally returns to the heat storage water tank 19.
Example 3 is capable of producing ultra-high temperature hot water above 90 ℃, and will be very competitive in the high temperature industry because of the high efficiency of the gas heat pump.
In the above embodiments, all components of the refrigeration cycle are not fully shown, and in the implementation process, common refrigeration accessories such as a liquid storage device, a filter, a dryer and the like are arranged in the refrigerant circuit, which cannot be regarded as substantial improvements of the present invention, and the present invention shall fall into the protection scope of the present invention.
The previous description of the embodiments is provided to facilitate a person of ordinary skill in the art in order to make and use the present invention. It will be apparent to those skilled in the art that various modifications can be readily made to these embodiments and the generic principles described herein may be applied to other embodiments without the use of the inventive faculty. Therefore, the present invention is not limited to the above-described embodiments, and those skilled in the art, based on the present disclosure, should make improvements and modifications without departing from the scope of the present invention.
Claims (8)
1. The high-temperature gas heat pump system with the mechanical supercooling is characterized by comprising a heat pump subsystem, an internal combustion engine subsystem, a linkage unit and a water supply flow path;
The heat pump subsystem consists of a heat pump main cycle and a mechanical supercooling sub cycle, wherein the heat pump main cycle consists of a refrigerant channel comprising a low-temperature evaporator, a four-way reversing valve, a gas-liquid separator, a first compressor, a refrigerant channel of a first condenser, a high-temperature channel of a supercooler and a first throttle valve which are sequentially connected in series through pipelines, and the first throttle valve is connected with the refrigerant channel of the low-temperature evaporator again to form a cycle;
The internal combustion engine subsystem consists of an engine, a flue gas flow path and a cooling liquid circulation flow path, wherein the flue gas flow path consists of an exhaust pipe of the engine, a flue gas channel of a three-way catalyst, a flue gas channel of a first flue gas heat exchanger, a flue gas channel of a second flue gas heat exchanger and a flue gas channel of the low-temperature evaporator which are sequentially connected in series through pipelines, and low-temperature flue gas is finally discharged from the low-temperature evaporator;
the linkage unit consists of a first electromagnetic clutch, a second electromagnetic clutch, a first belt pulley and a second belt pulley, wherein the first electromagnetic clutch is connected with an input shaft of the first compressor and is connected with an output shaft of the engine through the first belt pulley;
The water supply flow path is formed by sequentially connecting a heat storage water tank, a water pump, a secondary refrigerant channel of the first condenser, a secondary refrigerant channel of the second condenser, a secondary refrigerant channel of the cooling liquid heat exchanger and a secondary refrigerant channel of the second flue gas heat exchanger in series through pipelines, and then returning to the heat storage water tank;
The high-temperature gas heat pump system has two modes of high-temperature heat supply and defrosting:
A high-temperature heat supply mode, wherein a channel 2A of the four-way reversing valve 2 is communicated with a channel 2D, and a channel 2B is communicated with a channel 2C;
In the main circulation of the heat pump, a low-temperature low-pressure liquid refrigerant absorbs heat and evaporates in the low-temperature evaporator to absorb low-grade heat energy of ambient air, then the low-temperature low-pressure liquid refrigerant enters the gas-liquid separator through the four-way reversing valve, the refrigerant gas is compressed into high-temperature high-pressure gas through the first compressor, the high-temperature high-pressure gas heats backwater in the first condenser, the backwater is further cooled through the subcooler by a mechanical supercooling subcycler, finally the backwater is changed into low-temperature low-pressure liquid through the first throttle valve, and the low-temperature low-pressure liquid refrigerant reenters the low-temperature evaporator for next circulation;
in the defrosting mode, a four-way reversing valve channel 2A of the heat pump main cycle is communicated with a channel 2B, and a channel 2C is communicated with a channel 2D;
The mechanical supercooling sub-cycle stops working, and the working process of the heat pump main cycle is that high-temperature and high-pressure gas discharged from the first compressor enters the low-temperature evaporator through the four-way reversing valve to perform condensation heat release, and a coil pipe of the low-temperature evaporator is defrosted; the high-pressure gas is changed into low-temperature low-pressure liquid through the second throttle valve, and then enters the first condenser to absorb heat by evaporation and absorb heat of backwater;
the low-temperature evaporator is a refrigerant-air/flue gas heat exchanger and is provided with a refrigerant channel and an air/flue gas channel, and the subcooler is a refrigerant-refrigerant heat exchanger and is provided with a double-refrigerant channel.
2. The high temperature gas heat pump system of claim 1 wherein said first condenser and said second condenser are refrigerant-to-coolant heat exchangers having refrigerant channels and coolant channels, and wherein said first throttle valve and said second throttle valve are electronic expansion valves.
3. The high temperature gas heat pump system of claim 1 wherein the three-way catalyst has a flue gas channel and a coolant channel, wherein the first and second flue gas heat exchangers are coolant-flue gas heat exchangers having a coolant channel and a flue gas channel, wherein the coolant heat exchanger is a refrigerant-coolant heat exchanger having dual coolant channels.
4. The high temperature gas heat pump system according to claim 1, wherein the first compressor is a gas-supplementing enthalpy-increasing compressor, and has a suction port, a discharge port and a gas-supplementing port, and wherein a flash tank is disposed in the heat pump main cycle, the first throttle valve is connected to a liquid inlet of the flash tank, a liquid outlet of the flash tank is connected to an inlet of a third throttle valve, an outlet of the third throttle valve is connected to a refrigerant channel of the low temperature evaporator, and a gas outlet of the flash tank is connected to the gas-supplementing port of the first compressor.
5. The high-temperature gas heat pump system according to claim 1, wherein the working process of the flue gas flow path is that high-temperature flue gas exhausted by an exhaust pipe of the engine firstly enters a flue gas channel of the three-way catalyst, is catalytically converted into carbon dioxide, water and nitrogen and exchanges heat with cooling liquid, then firstly enters a flue gas channel of the first flue gas heat exchanger to exchange heat with the cooling liquid, then enters a flue gas channel of the second flue gas heat exchanger to exchange heat with backwater, finally enters a flue gas channel of the low-temperature evaporator, and finally is exhausted from the low-temperature evaporator.
6. The high-temperature gas heat pump system according to claim 1, wherein the working process of the cooling liquid circulation loop is that low-temperature cooling liquid enters the cylinder sleeve to exchange heat and cool the engine, then the low-temperature cooling liquid sequentially passes through the secondary refrigerant channel of the three-way catalyst and the secondary refrigerant channel of the first flue gas heat exchanger to absorb the waste heat of high-temperature flue gas, then the waste heat is sent into the high-temperature channel of the cooling liquid heat exchanger through the cooling liquid circulation pump to exchange heat with backwater from the second condenser to cool, and then the waste heat enters the cylinder sleeve again to perform the next circulation.
7. The high temperature gas heat pump system according to claim 1, wherein the water supply flow path is operated by introducing backwater into the heat storage tank, then introducing the backwater into the secondary refrigerant channel of the first condenser through the water pump, heating the backwater by the primary circulation of the heat pump, introducing the backwater into the secondary refrigerant channel of the second condenser, heating the backwater by the secondary circulation of the mechanical supercooling particles, then introducing the backwater into the secondary refrigerant channel of the coolant heat exchanger and the secondary refrigerant channel of the second flue gas heat exchanger, continuing to heat the backwater to a heating temperature, and finally introducing the backwater into the heat storage tank for supplying.
8. The high temperature gas heat pump system of claim 1 wherein said second flue gas heat exchanger is eliminated, wherein said internal combustion engine subsystem is comprised of said engine, said flue gas flow path and said coolant circulation flow path, wherein said flue gas flow path comprises an exhaust pipe of said engine, a flue gas passage of said three way catalyst, a flue gas passage of said first flue gas heat exchanger and a flue gas passage of said low temperature evaporator in series in this order, wherein said coolant circulation flow path comprises a high temperature passage of said coolant heat exchanger, said cylinder liner and said coolant circulation pump in series in this order, wherein said coolant circulation pump is in series with said high temperature passage of said coolant heat exchanger to form a cycle, wherein said water supply flow path comprises said heat storage tank, said water pump, a coolant passage of said first condenser, a coolant passage of said second condenser and a coolant passage of said coolant heat exchanger in series in this order, and wherein said coolant circulation flow path is subsequently in series with said high temperature passage of said coolant heat exchanger, said cylinder liner and said coolant circulation pump, wherein said coolant circulation pump is in series with said coolant passage of said three way catalyst heat exchanger, and wherein said coolant circulation pump is in series and is subsequently returned to said heat storage tank.
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| CN114719458B (en) * | 2022-04-08 | 2024-11-15 | 哈尔滨工业大学 | A quasi-two-stage compression gas heat pump unit with adjustable air supply suitable for severe cold regions |
| CN115264578A (en) * | 2022-07-28 | 2022-11-01 | 上海本家空调系统有限公司 | Heat accumulation type heat source station |
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