CN215832229U - High-temperature type gas heat pump system with mechanical supercooling function - Google Patents

Abstract

The utility model relates to a high-temperature type 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 heat pump subsystem is connected with the internal combustion engine subsystem through a pipeline; the main cycle 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 subcooler and a first throttle valve in series through pipelines; the mechanical sub-supercooling cycle is formed by connecting a low-temperature channel comprising the subcooler, a second compressor, a second condenser and a second throttling valve in series in sequence through pipelines; the internal combustion engine subsystem consists of an engine, a flue gas flow path and a cooling liquid circulating flow path. The utility model has high utilization rate of primary energy, can recover the residual heat of the main cycle of the heat pump, provides higher heat supply temperature, obviously improves the heat exchange uniformity of the system, reduces the irreversible loss of heat exchange, prevents an outdoor evaporator from frosting easily, and obviously improves the reliability and the service life of an engine.

Description

High-temperature type gas heat pump system with mechanical supercooling function

Technical Field

The utility model relates to a gas heat pump system, in particular to a high-temperature type gas heat pump system with mechanical supercooling.

Background

Natural gas plays an important role in energy revolution in China as a clean energy source. The natural gas system innovation is steadily promoted in China, and the application and the development of natural gas are crucial to the improvement of the energy utilization rate by adopting an efficient energy-saving technology.

The gas heat pump integrates two mature technologies of an engine and a steam compression type circulating device, and greatly expands the development space and market demand of a gas technology. The gas heat pump drives the compressor by using a gas engine to pump heat from a low-temperature heat source to a high-temperature heat source, and is a high-efficiency energy-saving device for improving the utilization rate of primary energy; meanwhile, the waste heat generated by the gas internal combustion engine can be further used for heat supply, and the heat energy conversion efficiency is high.

For the industrial process with the heat supply demand exceeding 80 ℃, the common heat pump system on the market at present needs to adopt a special high-temperature compressor with high cost, and heat pumps such as carbon dioxide and the like are not yet on large-scale marketization due to the difficulties of high-pressure control, high cost and the like. Compared with the prior art, the waste heat of the engine of the gas heat pump belongs to the high-temperature waste heat range, and if the waste heat is directly used for heating the heat exchange fluid, high-temperature or ultrahigh-temperature heat supply can be further realized. Thus, in high temperature industrial processes, gas heat pumps have significant technical and cost advantages.

However, due to the characteristics of application scenarios such as drying, the heat exchange fluid usually adopts a circulation heating mode, and the temperature of the heat exchange fluid entering the gas heat pump is also high. Thus, although 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 usually adopts a mode that a single engine drives a single compressor, and for a single-stage heat pump system, the overhigh temperature before a valve causes obvious throttling loss and reduces the energy efficiency of the system, thereby reducing the primary energy utilization efficiency of the gas heat pump. Meanwhile, for an application scene with large temperature difference between supply water and return water, the two-stage heat supply of the waste heat of the heat pump and the engine cannot well ensure the uniformity of a temperature difference field, so that large 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 problem influencing the performance of the unit. When the electrically-driven heat pump operates in winter, defrosting needs to be carried out in time, extra electric power is consumed, and the heating effect is influenced. Generally, the defrosting is needed once every 30-120 minutes, and the electricity consumption is increased by 10%.

SUMMERY OF THE UTILITY MODEL

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 utility model provides a high-temperature type gas heat pump system with mechanical supercooling.

The purpose of the utility model can be realized by the following technical scheme:

a high-temperature gas heat pump system with 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 sub-refrigeration cycle; the main cycle 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 subcooler and a first throttle valve in series through pipelines, and the first throttle valve is connected with the refrigerant channel of the low-temperature evaporator to form a cycle; the mechanical sub-supercooling cycle is formed by sequentially connecting a low-temperature channel comprising the subcooler, a second compressor, a second condenser and a second throttling valve in series through pipelines, and the second throttling valve is connected with the low-temperature channel of the subcooler to form a cycle;

the internal combustion engine subsystem consists of an engine, a flue gas flow path and a cooling liquid circulating flow path; the smoke flow path is formed by sequentially connecting an exhaust pipe of the engine, a smoke channel of the three-way catalyst, a smoke channel of the first smoke heat exchanger, a smoke channel of the second smoke heat exchanger and a smoke channel of the low-temperature evaporator in series through pipelines, and low-temperature smoke is finally discharged from the low-temperature evaporator; the cooling liquid circulation flow path is formed by sequentially connecting a high-temperature channel of a cooling liquid heat exchanger, a cylinder sleeve, a secondary refrigerant channel of the three-way catalyst, a secondary refrigerant channel of the first flue gas heat exchanger and a cooling liquid circulation pump in series through pipelines, and the cooling liquid circulation pump is connected with the high-temperature channel of the cooling liquid heat exchanger to form circulation;

the linkage unit consists of a first electromagnetic clutch, a second electromagnetic clutch, a first belt pulley and a second belt pulley; 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 a first belt pulley; the second electromagnetic clutch is connected with an input shaft of the second compressor and is connected with an output shaft of the engine through a second belt pulley; the engine drives the first compressor and the second compressor through a belt pulley and an electromagnetic clutch;

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 returns to the heat storage water tank.

The utility model has the characteristics that:

(1) a gas engine is adopted to drive a heat pump system to heat, so that high-temperature hot water suitable for industrial drying is generated; (2) overlapping a mechanical sub-cooling circulation at the outlet of the main circulation condenser, recovering the residual heat of the main circulation condenser and providing higher heating temperature; (3) based on the temperature field uniformity matching principle, according to different heat supply temperature levels of waste heat of a heat pump unit and a gas engine, the hot water temperature is increased by adopting a step heating mode; (4) a single gas engine is adopted to drive two compressors; (5) and introducing the low-temperature flue gas (50-70 ℃) subjected to heat recovery into an outdoor evaporation coil to prevent frosting.

Compared with the prior art, the utility model has the beneficial effects that:

the utility model adopts the internal combustion engine to drive the heat pump to absorb the environmental heat, simultaneously recovers the high-temperature waste heat of the engine, reduces the condensation temperature of the heat pump, and has high utilization rate of primary energy and high water supply temperature; by adopting the mechanical supercooling subsystem, the residual heat of the main cycle of the heat pump can be recovered, the throttling loss is reduced, the hot water from the main cycle is further heated, a higher heating temperature is provided, and the energy efficiency of the heat pump system is further improved; the condensation temperature of the main circulation is also reduced compared with a single-machine system; by adopting the step heating mode, the heat exchange uniformity of the system is obviously improved, the irreversible loss of heat exchange is reduced, and the energy efficiency of the system is obviously improved compared with that of an electrically-driven heat pump under the same heat supply temperature; due to the coupling relation of the two compressors, the capacity regulation characteristics of the two compressors are kept consistent, the regulation trend of the rotating speed is the same, the load operation characteristics are good, and stable and high-precision energy regulation can be realized; the outdoor evaporator is not easy to frost: the air temperature outside the room is kept higher by using low-temperature smoke and waste heat of the engine, frost blockage of the coil is remarkably delayed, and normal operation at extremely low ambient temperature (-20 ℃) is ensured; meanwhile, the reliability and the service life of the engine are obviously improved due to the reduction of the number of the start and stop times of the unit; under the defrosting mode, the unit only absorbs the waste heat of the engine, the water temperature of the heat storage water tank is not influenced, and the continuous stability of the drying process can be better ensured.

Drawings

FIG. 1 is a schematic flow chart of a high-temperature heating mode in example 1 of the present invention;

FIG. 2 is a schematic flow chart of a defrosting mode according to embodiment 1 of the present invention;

FIG. 3 is a schematic flow chart of a high-temperature heating mode according to embodiment 2 of the present invention;

FIG. 4 is a schematic flow chart of a high-temperature heating mode according to embodiment 3 of the present invention;

in the figure, 1-a low-temperature evaporator, 2-a four-way reversing valve (4 channels are 2A, 2B, 2C and 2D respectively), a 3-a gas-liquid separator, 4-a first compressor (4A-an air suction port, 4B-an exhaust port and 4C-an air supplement port), 5-a first condenser, 6-a subcooler, 7-a second compressor (7A is an air suction port and 7B is an exhaust port), 8-a second condenser, 9-a second throttle valve, 10-a first throttle valve, 11-an engine, 12-a cylinder sleeve, 13-a three-way catalyst, 14-a first flue gas heat exchanger, 15-a second flue gas heat exchanger, 16-a cooling liquid heat exchanger, 17-a cooling liquid circulating pump, 18-a water pump, 19-a heat storage water tank and 20-a first electromagnetic clutch, 21-second electromagnetic clutch, 22-first pulley, 23-second pulley, 24-flash tank, 25-third throttle.

Detailed Description

The utility model is described in detail below with reference to the figures and specific embodiments.

As shown in fig. 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;

the heat pump subsystem consists of a heat pump main cycle and a mechanical sub-refrigeration cycle; the main circulation of the heat pump is formed by sequentially connecting 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 subcooler 6 and a first throttle valve 10 in series through pipelines, and the first throttle valve 10 is connected with the refrigerant channel of the low-temperature evaporator 1 to form a circulation; the subcooler 6 is arranged at the outlet of the first condenser 5 and is used for further condensing and subcooling the refrigerant; the mechanical sub-supercooling cycle is formed by sequentially connecting a low-temperature channel comprising the subcooler 6, a second compressor 7, a second condenser 8 and a second throttling valve 9 in series through pipelines, and the second throttling valve 9 is connected with the low-temperature channel of the subcooler 6 to form a cycle;

the internal combustion engine subsystem consists of an engine 11, a flue gas flow path and a cooling liquid circulating flow path; the flue gas flow path is formed by sequentially connecting an exhaust pipe of an engine 11, a flue gas channel of a three-way catalyst 13, a flue gas channel of a first flue gas heat exchanger 14, a flue gas channel of a second flue gas heat exchanger 15 and a flue gas channel of the low-temperature evaporator 1 in series through pipelines; the cooling liquid circulation flow path is formed by sequentially connecting a high-temperature channel of a cooling liquid heat exchanger 16, the cylinder sleeve 12, a secondary refrigerant channel of the three-way catalyst 13, a secondary refrigerant channel of the first flue gas heat exchanger 14 and a cooling liquid circulation pump 17 in series through pipelines, and the cooling liquid circulation pump 17 is connected with the high-temperature channel of the cooling liquid heat exchanger 16 to form circulation; the cylinder liner 12 is a cylindrical part disposed in a cylinder block hole of the engine 11, and is fastened by a cylinder head; the piston reciprocates in the inner hole and is cooled by cooling water outside;

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; 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 a 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 a second belt pulley 23; the engine 11 drives the first compressor 4 and the second compressor 7 through a belt pulley and an electromagnetic clutch;

the water supply flow path is formed by sequentially connecting a secondary refrigerant channel comprising a heat storage water tank 19, a water pump 18 and 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 returns to the heat storage water tank 19.

Further, the low-temperature evaporator 1 is a finned tube heat exchanger and is provided with a refrigerant channel and an air/flue gas channel.

Further, the subcooler 6 is a double pipe heat exchanger and has double refrigerant passages.

Further, the first condenser 5 and the second condenser 8 are refrigerant-secondary refrigerant heat exchangers having a refrigerant channel and a secondary refrigerant channel, and are commonly plate heat exchangers, double-pipe heat exchangers, and the like.

Further, the first throttle 10 and the second throttle 9 are electronic expansion valves for adjusting the refrigerant flow rate by controlling the degree of superheat of the outlet.

Further, the three-way catalyst 13 has a flue gas channel connected to an exhaust pipe of the engine and a coolant channel for exchanging heat with the coolant flowing therethrough, and 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 secondary refrigerant-flue gas heat exchangers, and are provided with secondary refrigerant channels and flue gas channels; because the flue gas flow is small, the common types can be a sleeve heat exchanger, a plate heat exchanger and the like.

Further, the coolant heat exchanger 16 is a refrigerant-coolant heat exchanger, and has two coolant channels, and the common types are a plate heat exchanger, a double-pipe heat exchanger, and the like.

The high-temperature type gas heat pump system with mechanical supercooling of example 1 has two modes of high-temperature heat supply and defrosting, and the detailed working flow is as follows:

firstly, in a high-temperature heat supply mode, as shown in fig. 1, a channel 2A of a 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 as follows: the gas is combusted 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 is as follows: in the main cycle of the heat pump, a low-temperature low-pressure liquid refrigerant absorbs heat and is vaporized in a low-temperature evaporator 1 to absorb low-grade heat energy of ambient air, then enters a gas-liquid separator 3 through a four-way reversing valve 2 to separate unvaporized liquid, so that the gas absorption and liquid entrainment of the compressor are prevented, the refrigerant gas enters a first compressor 4 to be compressed into high-temperature high-pressure gas, the high-temperature high-pressure gas heats return water in a first condenser 5, is further cooled by a mechanical sub-cooling cycle through a subcooler 6, is finally changed into a low-temperature low-pressure liquid refrigerant again through a first throttle valve 10, and enters the low-temperature evaporator 1 again to perform the next cycle; in the mechanical supercooling sub-cycle, the low-temperature and low-pressure liquid refrigerant absorbs heat and evaporates in the subcooler 6, recovers the heat of the high-temperature refrigerant fluid of the main cycle of the heat pump, is compressed into high-temperature and high-pressure gas by the second compressor 7, heats the backwater in the second condenser 8, finally becomes the low-temperature and low-pressure liquid refrigerant by the second throttle valve 9, and enters the subcooler 6 again for the next cycle.

The working process of the water supply flow path is as follows: the return water is firstly introduced into a heat storage water tank 19, then enters a secondary refrigerant channel of the first condenser 5 through a water pump 18, is heated by the primary heat pump main cycle, and then enters a secondary refrigerant channel of the second condenser 8 to be heated by the mechanical sub-cooling sub-cycle; then the coolant is sent to the coolant channel of the coolant heat exchanger 16 and the coolant channel of the second flue gas heat exchanger 15, is heated to the heating temperature by three-stage heating and four-stage heating, and finally enters the heat storage water tank 23 for discharging.

The working process of the flue gas flow path is as follows: the high-temperature flue gas discharged from the exhaust pipe of the engine 11 firstly enters the flue gas channel of the three-way catalyst 13, is converted into harmless carbon dioxide, water and nitrogen through catalysis, exchanges heat with the cooling liquid, then firstly enters the flue gas channel of the first flue gas heat exchanger 14 to exchange heat with the cooling liquid, then enters the flue gas channel of the second flue gas heat exchanger 15 to further heat the backwater, and finally is introduced into the flue gas channel of the low-temperature evaporator 1 to improve the evaporation temperature of the low-temperature evaporator 1, prevent the frosting of a coil pipe, and finally is discharged from the low-temperature evaporator 1.

The working process of the cooling liquid circulation loop is as follows: the 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 waste heat of the high-temperature flue gas, the temperature of the cooling liquid is raised at the moment, and then the cooling liquid is sent into the high-temperature channel of the cooling liquid heat exchanger 16 through the cooling liquid circulating pump 17 to exchange heat and cool with the return water from the second condenser 8; and then re-enters the cylinder liner 12 for the next cycle.

Second, defrost mode

In the utility model, the frost blockage of the coil of the low-temperature evaporator 1 can be remarkably delayed by utilizing the waste heat of the low-temperature smoke of the engine, but the unit still has the defrosting requirement when the unit runs for a long time under the extreme working condition. As shown in fig. 2, in the defrosting mode, the four- way reversing valve 2A and 2B and the four- way reversing valve 2C and 2D of the main cycle of the heat pump are communicated;

the working process of the main cycle of the heat pump is as follows: high-temperature and high-pressure gas discharged from the first compressor 4 enters the low-temperature evaporator 1 through the four-way reversing valve 2 to be condensed and released, a coil of the low-temperature evaporator 1 is defrosted, the high-pressure gas is changed into low-temperature and low-pressure liquid through the second throttling valve 10, then enters the first condenser 5 to be evaporated and absorbed, the heat of backwater is absorbed, finally enters the first compressor 4 again through the four-way reversing valve 2, and is re-compressed into high-temperature and high-pressure gas to be circulated next time.

In the defrosting mode, the mechanical super-cooling sub-cycle stops working, and the working process of the internal combustion engine subsystem is the same as that of the high-temperature heating mode.

The working process of the water supply flow path is as follows: the return water is sent to 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 sent to a cooling liquid heat exchanger 16 and a second flue gas heat exchanger 15 in sequence to be heated again, and finally is sent back to a 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 has the function of heat transportation, and the water temperature in the heat storage water tank is not affected.

Example 2

Compared with the embodiment 1, as shown in fig. 3, the first compressor 4 of the embodiment 2 is an air-supplying enthalpy-increasing compressor, and is provided with an air-supplying port 4C in addition to an air-supplying port 4A and an air-discharging port 4B; at this time, a flash tank 24 is arranged in the main cycle of the heat pump and is used for separating liquid refrigerant and gaseous refrigerant after primary throttling, and the flash tank 24 is provided with a liquid inlet, a liquid outlet and an air outlet; the first throttle valve 10 is firstly connected with a liquid inlet of the flash tank 24, a liquid outlet of the flash tank 24 is connected with an inlet of a third throttle valve 25, and an outlet of the third throttle valve 25 is connected with a refrigerant channel of the low-temperature evaporator 1; the outlet of the flash tank 24 is connected to the make-up gas port of the first compressor 4. The first throttling valve 10 performs primary throttling on the refrigerant, and the throttled refrigerant enters the flash tank 24; the third throttling valve 25 is used for carrying out secondary throttling on the liquid refrigerant separated from the flash tank 24; the first compressor 4 adopts an air-supplying 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 3

Compared with the embodiment 1, as shown in fig. 4, the internal combustion engine subsystem is provided with a second flue gas heat exchanger 15, and comprises an 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 a cooling liquid heat exchanger 16, the cylinder sleeve 12 and a 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 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 coolant heat exchanger 16 which are sequentially connected in series; and then the flue gas heat exchanger 14 is connected with the coolant channel of the three-way catalyst 13 in turn, 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 generating ultra-high temperature hot water of 90 ℃ or more, and will be very competitive in the high temperature industry due to the high efficiency of the gas heat pump.

In the above embodiments, all components of the refrigeration cycle are not completely shown, and in the implementation process, the common refrigeration accessories such as the liquid storage device, the filter, the dryer and the like are arranged in the refrigerant circuit, which cannot be regarded as substantial improvements made in the present invention, and shall fall into the protection scope of the present invention.

Claims (9)

1. A high-temperature gas heat pump system with 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 sub-refrigeration cycle; the heat pump main cycle is formed by sequentially connecting 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 subcooler (6) and a first throttle valve (10) in series through pipelines, and the first throttle valve (10) is connected with the refrigerant channel of the low-temperature evaporator (1) to form a cycle; the mechanical sub-supercooling cycle is formed by sequentially connecting a low-temperature channel comprising the subcooler (6), a second compressor (7), a second condenser (8) and a second throttling valve (9) in series through pipelines, and the second throttling valve (9) is connected with the low-temperature channel of the subcooler (6) to form a cycle;

the internal combustion engine subsystem consists of an engine (11), a flue gas flow path and a cooling liquid circulating flow path; the smoke flow path is formed by sequentially connecting an exhaust pipe of the engine (11), a smoke channel of the three-way catalyst (13), a smoke channel of the first smoke heat exchanger (14), a smoke channel of the second smoke heat exchanger (15) and a smoke channel of the low-temperature evaporator (1) in series through pipelines; the cooling liquid circulation flow path is formed by sequentially connecting a high-temperature channel of a cooling liquid heat exchanger (16), a cylinder sleeve (12), a secondary refrigerant channel of the three-way catalyst (13), a secondary refrigerant channel of the first flue gas heat exchanger (14) and a cooling liquid circulation pump (17) in series through pipelines, and the cooling liquid circulation pump (17) is connected with the high-temperature channel of the cooling liquid heat exchanger (16) to form circulation;

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); 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);

the water supply flow path is formed by sequentially connecting a secondary refrigerant channel containing a heat storage water tank (19), a water pump (18) and 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 returns to the heat storage water tank (19).

2. A high temperature type gas heat pump system according to claim 1, wherein the low temperature evaporator (1) is a fin tube heat exchanger provided with a refrigerant passage and an air/flue gas passage.

3. The high temperature type gas heat pump system according to claim 1, wherein the subcooler (6) is a double pipe heat exchanger provided with double refrigerant passages.

4. The high temperature type gas heat pump system according to claim 1, wherein the first condenser (5) and the second condenser (8) are refrigerant-coolant heat exchangers having refrigerant passages and coolant passages.

5. A high temperature type gas heat pump system according to claim 1, characterized in that the first throttle valve (10) and the second throttle valve (9) are electronic expansion valves.

6. The high temperature type gas heat pump system according to claim 1, wherein the three-way catalyst (13) has a flue gas passage and a coolant passage.

7. The high-temperature gas heat pump system according to claim 1, wherein the first flue gas heat exchanger (14) and the second flue gas heat exchanger (15) are coolant-flue gas heat exchangers having coolant channels and flue gas channels.

8. The high temperature type gas heat pump system according to claim 1, wherein the coolant heat exchanger (16) is a refrigerant-coolant heat exchanger having dual coolant channels.

9. The high temperature type gas heat pump system according to claim 1, wherein the first compressor (4) is an enthalpy-increasing vapor injection compressor having a suction port (4A), a discharge port (4B), and a charge port (4C); at the moment, a flash tank (24) is arranged in the main circulation of the heat pump; the first throttling valve (10) is connected with a liquid inlet of a flash tank (24), a liquid outlet of the flash tank (24) is connected with an inlet of a third throttling valve (25), and an outlet of the third throttling valve (25) is connected with a refrigerant channel of the low-temperature evaporator (1); and the gas outlet of the flash tank (24) is connected with the gas supplementing port of the first compressor (4).

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