CN108731295B - Heat recovery gas air conditioning system - Google Patents
Heat recovery gas air conditioning system Download PDFInfo
- Publication number
- CN108731295B CN108731295B CN201810605900.7A CN201810605900A CN108731295B CN 108731295 B CN108731295 B CN 108731295B CN 201810605900 A CN201810605900 A CN 201810605900A CN 108731295 B CN108731295 B CN 108731295B
- Authority
- CN
- China
- Prior art keywords
- heat exchanger
- port
- valve
- way valve
- pump
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Classifications
-
- 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
- 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
-
- 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
- F25B43/006—Accumulators
-
- 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
Landscapes
- 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)
- Heat-Pump Type And Storage Water Heaters (AREA)
- Other Air-Conditioning Systems (AREA)
Abstract
The invention discloses a heat recovery gas air conditioning system, the structure of the invention is simple, the cost is low, and the practicability is strong, the system includes: a refrigerant circulating system, a heat recovery system, a cooling liquid circulating system, a defrosting circulating system and an air conditioner water circulating system; compared with the traditional air conditioning system, the system can effectively improve the primary energy utilization rate, meanwhile, the refrigerant and the engine heat can be fully recovered under the refrigerating working condition, the system is particularly suitable for distinguishing the building structures of the inner zone and the outer zone, in addition, the defrosting does not influence the heating effect under the heating working condition, the water temperature fluctuation is reduced, the indoor comfort level is effectively improved, the working efficiency is improved, a large amount of cost is saved, and the system is suitable for popularization and use.
Description
Technical Field
The invention relates to an air conditioning system, in particular to a heat recovery gas air conditioning system, and belongs to the technical field of gas air conditioning application.
Background
An air conditioner is an assembly for providing a spatial area (typically an enclosure) with process air temperature variations. Its function is to regulate the parameters of temperature, humidity, cleanliness and air flow rate of air in the room (or enclosed space, zone) to meet the requirements of human body comfort or technological process. At present, the energy consumption of the air conditioner occupies a large part in the energy consumption of the building, so that how to improve the energy efficiency of the air conditioner and fully utilize various grade energy sources becomes an important direction for the research and development of the air conditioner and also becomes a key means for building energy conservation. Meanwhile, the energy efficiency of the conventional electrically-driven air conditioner is still quite low compared with the primary energy utilization rate, so how to improve the primary energy utilization rate of the air conditioning unit and reduce the energy waste is also important for developing the air conditioning system. The defrosting of the current air conditioning system mainly adopts the reversing defrosting of a four-way valve, the temperature of a use side can be reduced by the defrosting mode, energy waste is caused, and therefore, the heat recovery gas air conditioning system has a good market prospect.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provides a heat recovery gas air-conditioning system which is convenient to use and saves a large amount of cost.
In order to solve the technical problems, the invention provides the following technical scheme:
the invention provides a heat recovery gas air conditioning system, comprising: refrigerant circulation system, heat recovery system, coolant liquid circulation system, defrost cycle system, air conditioner water circulation system, refrigerant circulation system includes: compressor, heat exchanger, cross valve A, fin heat exchanger, expansion valve A and expansion valve B, check valve A and check valve B, reservoir, heat exchanger, vapour and liquid separator, heat recovery system includes: hot-water tank, pump A, heat exchanger, solenoid valve C and solenoid valve D, heat exchanger C, coolant liquid circulation system includes: engine assembly, pump B, three-way valve A and three-way valve B, heat exchanger B and heat exchanger C, radiator unit, defrost cycle system includes: heat exchanger A, pump A, defrosting subassembly, air conditioner water circulating system includes: the system comprises a heat exchanger, an air conditioner tail end, a pump, an electromagnetic valve A, an electromagnetic valve B, a heat exchanger B and a heat exchanger A.
As a preferred technical scheme of the invention, the exhaust of the compressor is connected with a heat exchanger, the heat exchanger is connected with an S port of a four-way valve, a C port of the four-way valve is connected with a finned heat exchanger, a D port of the four-way valve is connected with a gas-liquid separator, an E port of the four-way valve is connected with the S port of the four-way valve A, the C port of the four-way valve A is connected with a liquid storage device through a one-way valve, the D port of the four-way valve A is connected with the gas-liquid separator, the E port of the four-way valve A is connected with the heat exchanger, the finned heat exchanger is connected with the liquid storage device through an expansion valve A and a one-way valve B, the liquid storage device is connected with the heat exchanger through an expansion valve B and a one-way valve A, and the gas-liquid separator is connected with the suction of the compressor.
As a preferred technical scheme of the invention, the outlet of the pump A is divided into two paths and is respectively connected with the heat exchanger and the electromagnetic valve D, the heat exchanger is connected with the electromagnetic valve C, the electromagnetic valve C and the electromagnetic valve D are converged and then are connected with the heat exchanger C, the heat exchanger C is connected with the hot water tank, and the hot water tank is connected with the inlet of the pump A.
As a preferred technical scheme of the invention, the outlet of the pump B is divided into two paths and is respectively connected with the port C of the three-way valve B and the heat exchanger C, the port A of the three-way valve B is connected with the port B of the three-way valve A, the engine component is connected with the inlet of the pump B, the heat exchanger C is connected with the heat exchanger B, the heat exchanger B is divided into two paths and is respectively connected with the port B of the three-way valve A and the heat dissipation component, and the heat dissipation component is connected with the port C of the three-way valve A.
As a preferred technical solution of the present invention, an outlet of the pump a is connected to a defrosting assembly, the defrosting assembly is connected to a heat exchanger a, and the heat exchanger a is connected to an inlet of the pump a.
As a preferred technical scheme of the invention, the air-conditioning water at the tail end of the air conditioner is connected with a pump inlet, the pump outlet branch is respectively connected with a heat exchanger and a solenoid valve B, the solenoid valve B is connected with the heat exchanger B, the heat exchanger B is connected with a heat exchanger A, and the heat exchanger A is connected with the tail end of the air conditioner after being converged with the heat exchanger through the solenoid valve A.
The invention has the following beneficial effects: the invention has simple structure, low cost and strong practicability, and 1, the heat of the engine cylinder sleeve, the heat of smoke and the heat released to the environment by refrigeration are fully recovered to prepare hot water, thereby reducing the waste of energy; 2. reasonably coordinating the relationship between the refrigerating capacity and the hot water capacity (under the working conditions of refrigeration and hot water, hot water is mainly used or refrigeration is mainly used); 3. the temperature of the cooling liquid returning to the engine is kept constant, and the stable and reliable operation of the engine is guaranteed; 4. when the system is defrosted, the heating is continued, and the heating quantity is not attenuated; 5. the system directly adopts a gas or oil engine to drive the compressor, so that a large amount of energy transmission loss in the middle is reduced, a large amount of waste heat and smoke condensation heat are recovered, the primary energy utilization rate is greatly improved, a large amount of cost is saved, the system is simple and convenient to use, has good economic and social benefits, and is suitable for popularization and use.
Drawings
The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention and together with the description serve to explain the principles of the invention and not to limit the invention. In the drawings:
FIG. 1 is a schematic view of the subjective structure of the present invention;
FIG. 2 is a schematic view of a refrigeration configuration of the refrigerant cycle system of the present invention;
FIG. 3 is a schematic view of a heating structure of the refrigerant cycle system of the present invention;
FIG. 4 is a schematic diagram of a hot water configuration of the refrigerant cycle system of the present invention;
FIG. 5 is a schematic diagram of the heat recovery system of the present invention;
FIG. 6 is a schematic view of the coolant circulation system of the present invention;
FIG. 7 is a schematic view of the defrost cycle system of the present invention;
fig. 8 is a schematic view of the air-conditioning water circulating water structure of the present invention;
in the figure: 1. a compressor; 2. a heat exchanger; 3. a four-way valve; 4. a four-way valve A; 5. a finned heat exchanger; 6. a heat dissipating component; 7. a defrost assembly; 8. a one-way valve; 9. an expansion valve A; 10. an expansion valve B; 11. a one-way valve A; 12. a check valve B; 13. a reservoir; 14. a gas-liquid separator; 15. a heat exchanger; 16. an air conditioner terminal; 17. a pump; 18. an electromagnetic valve A; 19. a solenoid valve B; 20. a pump A; 21. a heat exchanger A; 22. a heat exchanger B; 23. a heat exchanger C; 24. a hot water tank; 25. a pump A; 26. a three-way valve A; 27. a three-way valve B, 28 and a pump B; 29. an engine assembly; 30. a solenoid valve C; 31. and a solenoid valve D.
Detailed description of the preferred embodiments
The preferred embodiments of the present invention will be described in conjunction with the accompanying drawings, and it should be understood that they are presented herein only to illustrate and explain the present invention and not to limit the present invention.
Example (b): as shown in fig. 1 to 8, the present invention provides a heat recovery gas air conditioning system, comprising: refrigerant circulation system, heat recovery system, coolant liquid circulation system, defrosting circulation system, air conditioner water circulation system, refrigerant circulation system includes: compressor 1, heat exchanger 2, four-way valve 3, four-way valve A4, fin heat exchanger 5, expansion valve A9 and expansion valve B10, check valve A11 and check valve B12, reservoir 13, heat exchanger 15, vapour and liquid separator 14, heat recovery system includes: hot water tank 24, pump A25, heat exchanger 2, solenoid valve C30 and solenoid valve D31, heat exchanger C23, the coolant circulation system includes: the engine assembly 29, the pump B28, the three-way valve A26, the three-way valve B27, the heat exchanger B22, the heat exchanger C23 and the heat dissipation assembly 6, and the defrosting circulation system comprises: heat exchanger A21, pump A20, defrosting subassembly 7, air conditioner water circulating system includes: heat exchanger 15, air conditioner terminal 16, pump 17, solenoid valve A18 and solenoid valve B19, heat exchanger B22 and heat exchanger A21.
In order to enable the heat recovery gas air-conditioning system to be convenient to use and high in working efficiency, the exhaust gas of the compressor 1 is connected with the heat exchanger 2, the heat exchanger 2 is connected with the S port of the four-way valve 3, the C port of the four-way valve 3 is connected with the finned heat exchanger 5, the D port is connected with the gas-liquid separator 14, the E port is connected with the S port of the four-way valve A4, the C port of the four-way valve A4 is connected with the liquid storage device 13 through the one-way valve 8, the D port is connected with the gas-liquid separator 14, the E port is connected with the heat exchanger 15, the finned heat exchanger 5 is connected with the liquid storage device 13 through the expansion valve A9 and the one-way valve B12, the liquid storage device 13 is connected with the heat exchanger 15 through the expansion valve B10 and the one-way valve A11, the gas-liquid separator 14 is connected with the compressor 1 in a gas suction manner, the outlet of the pump A25 is divided into two paths to be respectively connected with the heat exchanger 2 and the electromagnetic valve D31, the heat exchanger 2 is connected with the electromagnetic valve C30, the electromagnetic valve C30 is connected with the heat exchanger C23 after the electromagnetic valve D31 is converged, the heat exchanger C23 is connected with a hot water tank 24, the hot water tank 24 is connected with an inlet of a pump A25, an outlet of the pump B28 is divided into two paths and is respectively connected with a port C of a three-way valve B27 and the heat exchanger C23, a port A of the three-way valve B27 is connected with a port B of the three-way valve A26, the engine assembly 29 is connected with an inlet of the pump B28, the heat exchanger C23 is connected with a heat exchanger B22, the heat exchanger B22 is divided into two paths and is respectively connected with a port B of the three-way valve A26 and a heat dissipation assembly 6, the heat dissipation assembly 6 is connected with a port C of the three-way valve A26, an outlet of the pump A20 is connected with a defrosting assembly 7, the defrosting assembly 7 is connected with a heat exchanger A21, the heat exchanger A21 is connected with an inlet of a pump A20, the air conditioning water at the air conditioner tail end 16 is connected with an inlet of the pump 17, an outlet of the pump 17 is divided into 2 paths and is respectively connected with a heat exchanger 15 and an electromagnetic valve B19, the electromagnetic valve B19 is connected with the heat exchanger B22, the heat exchanger B22 is connected with the heat exchanger A21, and the heat exchanger A21 is converged with the heat exchanger 15 through the electromagnetic valve A18 and then is connected with the tail end 16 of the air conditioner.
When the four-way valve is used, a refrigerant is compressed into high-temperature and high-pressure refrigerant steam in a compressor 1 and is discharged from an exhaust port to enter a heat exchanger 2, if the working condition is refrigeration, the refrigerant enters an S port of the four-way valve 3 through the heat exchanger 2 (no water flows through the heat exchanger), and if the working condition is refrigeration and hot water (refrigeration is mainly) working condition, the refrigerant exchanges heat with water entering the heat exchanger in the heat exchanger 2 and then enters the S port of the four-way valve 3; refrigerant enters the finned heat exchanger 5 through a port C of the four-way valve 3 to exchange heat with outdoor air and is condensed into high-pressure refrigerant liquid, and the high-pressure refrigerant liquid enters the liquid storage device 13 through the one-way valve B12; refrigerant liquid in the liquid storage device 13 is throttled and depressurized by an expansion valve B10 to form low-pressure refrigerant liquid which enters a heat exchanger 15; the low-pressure refrigerant liquid is evaporated in the heat exchanger 15 to absorb the heat of the air-conditioning water, and then becomes low-temperature low-pressure refrigerant steam which enters the gas-liquid separator 14 through the E port and the D port of the four-way valve A4, and the purpose of reducing the temperature of the air-conditioning water is achieved; the refrigerant is subjected to gas-liquid separation in the gas-liquid separator 14, and the gaseous refrigerant enters the compressor to continue to circulate.
Referring to fig. 3, the refrigerant is compressed into high-temperature high-pressure refrigerant vapor in the compressor 1, and the high-temperature high-pressure refrigerant vapor is discharged from the exhaust port and enters the heat exchanger 2, and if the refrigerant is in a refrigeration working condition, the refrigerant enters the S port of the four-way valve 3 through the heat exchanger 2 (no water flows through the heat exchanger), enters the S port of the four-way valve A4 through the E port, and then enters the heat exchanger 15 through the E port; the refrigerant exchanges heat with air-conditioning water in the heat exchanger 15 and is condensed into high-pressure refrigerant liquid, the high-pressure refrigerant liquid enters the liquid reservoir 13 through the one-way valve A11, and meanwhile, the air-conditioning water absorbs heat and is heated for user heating; refrigerant liquid in the liquid storage device 13 is throttled and decompressed by an expansion valve A9 to form low-pressure refrigerant liquid which enters the fin heat exchanger 5; the low-pressure refrigerant liquid is evaporated in the fin heat exchanger 5 to absorb the heat of outdoor air, and then becomes low-temperature low-pressure refrigerant steam which enters the gas-liquid separator 14 through the port C and the port D of the four-way valve 3; the refrigerant is subjected to gas-liquid separation in the gas-liquid separator 14, and the gaseous refrigerant enters the compressor to continue to circulate.
Referring to fig. 4, the refrigerant is compressed into high-temperature and high-pressure refrigerant vapor in the compressor 1, and the high-temperature and high-pressure refrigerant vapor is discharged from the exhaust port and enters the heat exchanger 2, exchanges heat with water entering the heat exchanger in the heat exchanger 2, is condensed into high-pressure refrigerant liquid, enters the S port of the four-way valve 3, enters the S port of the four-way valve A4 through the E port, and then enters the liquid reservoir 13 through the check valve 8 through the C port; the refrigerant liquid in the accumulator 13 is divided into two cases: one is only in a hot water working condition, the expansion valve B10 is fully closed, refrigerant liquid is throttled and depressurized by the expansion valve A9 to form low-pressure refrigerant liquid, the low-pressure refrigerant liquid enters the fin heat exchanger 5 to be evaporated and absorb heat of outdoor air, then low-temperature low-pressure refrigerant steam enters the gas-liquid separator 14 through the port C and the port D of the four-way valve 3, gas-liquid separation is realized in the gas-liquid separator 14, and gaseous refrigerant enters the compressor to continue to circulate; the other is a hot water + refrigeration (hot water is the main) working condition, and the refrigerant liquid is divided into two paths: one path of low-pressure refrigerant liquid which is throttled and decompressed by an expansion valve B10 enters a heat exchanger 15 to be evaporated and absorb the heat of air-conditioning water, and then low-temperature low-pressure refrigerant steam enters a gas-liquid separator 14 through an opening E and an opening D of a four-way valve A4, and the purpose of reducing the temperature of the air-conditioning water is achieved; the other path of refrigerant is throttled and decompressed by an expansion valve A9 to form low-pressure refrigerant liquid, the low-pressure refrigerant liquid enters a fin heat exchanger 5 to be evaporated and absorb heat of outdoor air, then low-temperature low-pressure refrigerant steam enters a gas-liquid separator 14 through a port C and a port D of a four-way valve 3, gas-liquid separation of the refrigerant is realized in the gas-liquid separator 14, and gaseous refrigerant enters a compressor to continue to circulate. The flow of the two paths of refrigerants is comprehensively regulated by controlling the expansion valve A9 and the expansion valve B10 by the controller according to the hot water demand and the refrigeration demand.
Referring to fig. 5, a heat recovery system is shown, the system comprising: the hot water tank 24, the pump A25, the heat exchanger 2, the electromagnetic valve C30, the electromagnetic valve D31 and the heat exchanger C23, wherein the outlet of the pump A25 is divided into two paths to be respectively connected with the heat exchanger 2 and the electromagnetic valve D31; the heat exchanger 2 is connected with an electromagnetic valve C30; the electromagnetic valve C30 and the electromagnetic valve D31 are converged and then connected with the heat exchanger C23; the heat exchanger C23 is connected with a hot water tank 24; the hot water tank 24 is connected to the inlet of a pump a 25. If a heat recovery system is completed, the system can effectively recover cylinder sleeve water, smoke and heat of a refrigerant under a refrigeration working condition of an engine, the system is mainly used for preparing hot water, water in a hot water tank 24 is divided into two paths after passing through a pump A25, and when the heat in the refrigerant needs to be recovered (an electromagnetic valve D31 is closed, an electromagnetic valve C30 is opened), the water enters a heat exchanger 2 to absorb the heat of the refrigerant, the temperature of the water is raised, then the water enters a heat exchanger C23 to continuously absorb the heat of cooling liquid, the temperature of the water is raised, and finally the water returns to the hot water tank 24; when the heat in the refrigerant does not need to be recovered (the electromagnetic valve D31 is opened, and the electromagnetic valve C30 is closed), the water from the hot water tank directly enters the heat exchanger C23 to absorb the heat of the cooling liquid, and the water returns to the hot water tank 24 after the temperature is raised. The hot water in the hot water tank can be used for domestic hot water, and can also be used for other purposes such as heating or preheating. When the water in the hot water tank 24 reaches the set temperature, the pump a25 is controlled to stop running, and when the temperature is reduced, the pump a25 is started to continue recovering heat.
Referring to fig. 6, a coolant circulation system is shown, the system comprising: the heat dissipation assembly comprises an engine assembly 29 (comprising an engine, a flue gas heat recovery device and the like), a pump B28, a three-way valve A26, a three-way valve B27, a heat exchanger B22, a heat exchanger C23 and a heat dissipation assembly 6, wherein the outlet of the pump B28 is divided into two paths and is respectively connected with a port C of the three-way valve B27 and the heat exchanger C23; the port A of the three-way valve B27 is connected with the engine assembly 29, and the port B is connected with the port A of the three-way valve A26; the engine assembly 29 is connected with the inlet of the pump B28; the heat exchanger C23 is connected with the heat exchanger B22; the heat exchanger B22 is divided into two paths and is respectively connected with a port B of the three-way valve A26 and the heat dissipation assembly 6; the radiator module 6 is connected with the port C of the three-way valve A26. If the coolant circulation system is completed, the coolant heated by absorbing heat in the engine assembly 29 is divided into two paths by the pump B28: when the temperature is lower than the set temperature of the engine coolant, the coolant directly returns to the engine through the port C and the port A of the three-way valve B27; when the temperature is higher than the set temperature of the return engine coolant, the flow rates entering the three-way valve B27 from the ports C and B are adjusted by adjusting the proportion of the three-way valve B27, respectively, with the ultimate aim of maintaining the temperature of the return engine coolant at the set value. The cooling liquid enters a heat exchanger C23 and a heat exchanger B22 to reduce the heat release temperature, and the cooling liquid after heat release is divided into two paths: when the temperature is lower than the set temperature of the engine coolant, controlling the connection of the port A and the port B of the three-way valve A26, mixing the high-temperature coolant from the coolant passing through the ports B of the three-way valve A26 and the three-way valve B27 and the port C of the three-way valve B27 to the set temperature of the engine coolant, and allowing the coolant to enter the engine assembly 29 to continuously absorb heat; when the temperature is higher than the set temperature of the engine coolant, the opening A and the opening C of the three-way valve A26 are controlled to be communicated, the coolant enters the heat dissipation assembly 6 to release heat to the environment, then the coolant passes through the openings B of the three-way valve A26 and the three-way valve B27 and is mixed with the high-temperature coolant from the opening C of the three-way valve B27 to reach the set temperature of the engine coolant to continuously absorb heat, the system mainly takes out heat in cylinder liner water and smoke of the engine and releases heat to a heat recovery system, a defrosting circulation system and the environment, so that the temperature of the coolant returning to the engine is controlled at the temperature favorable for efficient operation of the engine, and the reliability and the economy of the operation of the engine are improved.
Referring to fig. 7, a defrost cycle system is shown, the system comprising: the defrosting device comprises a heat exchanger A21, a pump A20 and a defrosting assembly 7, wherein the outlet of the pump A20 is connected with the defrosting assembly 7; the defrosting assembly 7 is connected with a heat exchanger A21; the heat exchanger a21 is connected to the inlet of the pump a 20. If the defrost cycle is complete, pump A20 is activated when the system reaches defrost conditions. In the heat exchanger a21, the defrosting water absorbs the heat of the air-conditioning water heated by the heat exchanger B22, the temperature of the air-conditioning water rises, and the air enters the defrosting assembly 7 through the pump a20, the defrosting water heats the air passing through the fin heat exchanger 5 in the defrosting assembly 7, the temperature of the air is raised, and the air returns to the heat exchanger a21 to continue circulation. The heated air achieves the purpose of defrosting in the heat exchange process of the fin heat exchanger 5, so that the heating performance of the system cannot be influenced by defrosting because the system still heats when defrosting. Effectively ensures that the heating capacity is not attenuated when the system defrosts
Referring to fig. 8, there is shown an air conditioning water circulation system, the system including: the heat exchanger 15, the air-conditioning tail end 16, the pump 17, the electromagnetic valves A18 and 19 and the heat exchangers B22 and 21, wherein the air-conditioning water at the air-conditioning tail end 16 is connected with an inlet of the pump 17; the outlet of the pump 17 is divided into 2 paths which are respectively connected with the heat exchanger 15 and the electromagnetic valve B19; the electromagnetic valve B19 is connected with the heat exchanger B22; the heat exchanger B22 is connected with the heat exchanger A21; the heat exchanger A21 is connected with the air conditioner tail end 16 after being converged with the heat exchanger 15 through the electromagnetic valve A18. The purpose of refrigerating or heating the user side by the air conditioning water is realized, and during the refrigeration (the electromagnetic valves A18 and A19 are closed all the time): the air-conditioning water enters the heat exchanger 15 for cooling through the pump 17 after absorbing heat at the air-conditioning tail end 16, the air-conditioning water after cooling continues to enter the air-conditioning tail end for absorbing heat, and during heating: the air conditioning water is divided into two paths by a pump 17 after releasing heat at an air conditioning tail end 16: one path enters the heat exchanger 15 to absorb heat and then returns to the air conditioner terminal 16 to release heat (when the electromagnetic valves A18 and 19 are closed, only the path exists); the other path of air-conditioning water enters a heat exchanger B22 after passing through an electromagnetic valve B19 to absorb heat for heating, the heated air-conditioning water is converged with the air-conditioning water absorbing heat in the heat exchanger 15 through a heat exchanger A21 and an electromagnetic valve A18 and then returns to the tail end of the air conditioner to release heat, and during defrosting: (solenoid valves A18 and 19 are always open): the air-conditioning water is divided into two paths by a pump 17 after releasing heat at an air-conditioning tail end 16: one path enters a heat exchanger 15 to absorb heat; the other path of the air conditioner water enters a heat exchanger B22 after passing through an electromagnetic valve B19 to absorb heat for heating, the heated air conditioner water releases heat to defrosting water in a heat exchanger A21, and the air conditioner water absorbing heat in a heat exchanger 15 after releasing heat is merged with the air conditioner water through an electromagnetic valve A18 and then returns to the tail end of the air conditioner to release heat.
Finally, it should be noted that: although the present invention has been described in detail with reference to the foregoing embodiments, it will be apparent to those skilled in the art that changes may be made in the embodiments and/or equivalents thereof without departing from the spirit and scope of the invention. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (1)
1. A heat recovery gas air conditioning system, comprising: refrigerant circulation system, heat recovery system, coolant liquid circulation system, defrosting circulation system, air conditioner water circulation system, refrigerant circulation system includes: compressor (1), first heat exchanger (2), cross valve (3), cross valve A (4), finned heat exchanger (5), expansion valve A (9) and expansion valve B (10), check valve A (11) and check valve B (12), reservoir (13), second heat exchanger (15), vapour and liquid separator (14), heat recovery system includes: hot-water tank (24), pump C (25), first heat exchanger (2), solenoid valve C (30) and solenoid valve D (31), heat exchanger C (23), coolant liquid circulation system includes: engine assembly (29), pump B (28), three-way valve A (26) and three-way valve B (27), heat exchanger B (22) and heat exchanger C (23), radiator unit (6), the defrost cycle system includes: heat exchanger A (21), pump A (20), defrosting subassembly (7), air conditioner water circulating system includes: a second heat exchanger (15), an air conditioner terminal (16), a pump (17), an electromagnetic valve A (18), an electromagnetic valve B (19), a heat exchanger B (22) and a heat exchanger A (21);
the exhaust of the compressor (1) is connected with a first heat exchanger (2), the first heat exchanger (2) is connected with an S port of a four-way valve (3), a C port of the four-way valve (3) is connected with a fin heat exchanger (5), a D port is connected with a gas-liquid separator (14), an E port is connected with an S port of the four-way valve A (4), the C port of the four-way valve A (4) is connected with a liquid storage device (13) through a one-way valve (8), the D port is connected with the gas-liquid separator (14), the E port is connected with a second heat exchanger (15), the fin heat exchanger (5) is connected with the liquid storage device (13) through an expansion valve A (9) and a one-way valve B (12), the liquid storage device (13) is connected with the second heat exchanger (15) through an expansion valve B (10) and a one-way valve A (11), and the gas-liquid separator (14) is connected with the compressor (1) in an air suction mode;
the outlet of the pump C (25) is divided into two paths and is respectively connected with a first heat exchanger (2) and an electromagnetic valve D (31), the first heat exchanger (2) is connected with an electromagnetic valve C (30), the electromagnetic valve C (30) and the electromagnetic valve D (31) are converged and then connected with a heat exchanger C (23), the heat exchanger C (23) is connected with a hot water tank (24), and the hot water tank (24) is connected with the inlet of the pump C (25);
the outlet of the pump B (28) is divided into two paths and is respectively connected with a port C of a three-way valve B (27) and a heat exchanger C (23), a port A of the three-way valve B (27) is connected with the port B, a port A of the three-way valve A (26) is connected with a cooling liquid outlet of an engine assembly, the engine assembly (29) is connected with the inlet of the pump B (28), the heat exchanger C (23) is connected with a heat exchanger B (22), the heat exchanger B (22) is divided into two paths and is respectively connected with a port B of the three-way valve A (26) and a heat dissipation assembly (6), and the heat dissipation assembly (6) is connected with the port C of the three-way valve A (26);
the outlet of the pump A (20) is connected with a defrosting assembly (7), the defrosting assembly (7) is connected with a heat exchanger A (21), and the heat exchanger A (21) is connected with the inlet of the pump A (20);
the air-conditioning water at the air-conditioning tail end (16) is connected with an inlet of a pump (17), an outlet of the pump (17) is divided into two paths to be connected with a second heat exchanger (15) and a solenoid valve B (19), the solenoid valve B (19) is connected with a heat exchanger B (22), the heat exchanger B (22) is connected with a heat exchanger A (21), and the heat exchanger A (21) is connected with the air-conditioning tail end (16) after being converged with the second heat exchanger (15) through a solenoid valve A (18).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810605900.7A CN108731295B (en) | 2018-06-13 | 2018-06-13 | Heat recovery gas air conditioning system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201810605900.7A CN108731295B (en) | 2018-06-13 | 2018-06-13 | Heat recovery gas air conditioning system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108731295A CN108731295A (en) | 2018-11-02 |
| CN108731295B true CN108731295B (en) | 2023-04-18 |
Family
ID=63929281
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201810605900.7A Active CN108731295B (en) | 2018-06-13 | 2018-06-13 | Heat recovery gas air conditioning system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108731295B (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109990499B (en) * | 2019-03-04 | 2021-02-19 | 南京天加环境科技有限公司 | Gas heat pump air conditioning system without shutdown during defrosting |
| CN111336684B (en) * | 2020-03-19 | 2021-09-10 | 佛山市顺德区思睿德电器有限公司 | Environment-friendly defrosting type air source gas heat pump |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1869553A (en) * | 2006-06-23 | 2006-11-29 | 东南大学 | Solar-gas engine heat pump heating device and its operation method |
| CN102788493A (en) * | 2012-08-30 | 2012-11-21 | 华北电力大学（保定） | Heat pump drier driven by gas engine |
| CN105674558A (en) * | 2016-02-16 | 2016-06-15 | 蓝焰高科（天津）燃气技术有限公司 | Gas engine driven steam compressing and absorbing combined type heat pump hot water unit running method |
| WO2017063321A1 (en) * | 2015-10-13 | 2017-04-20 | 东南大学 | Air source heat pump spray defrosting device based on super-hydrophobic finned tube heat exchanger |
-
2018
- 2018-06-13 CN CN201810605900.7A patent/CN108731295B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1869553A (en) * | 2006-06-23 | 2006-11-29 | 东南大学 | Solar-gas engine heat pump heating device and its operation method |
| CN102788493A (en) * | 2012-08-30 | 2012-11-21 | 华北电力大学（保定） | Heat pump drier driven by gas engine |
| WO2017063321A1 (en) * | 2015-10-13 | 2017-04-20 | 东南大学 | Air source heat pump spray defrosting device based on super-hydrophobic finned tube heat exchanger |
| CN105674558A (en) * | 2016-02-16 | 2016-06-15 | 蓝焰高科（天津）燃气技术有限公司 | Gas engine driven steam compressing and absorbing combined type heat pump hot water unit running method |
Also Published As
| Publication number | Publication date |
|---|---|
| CN108731295A (en) | 2018-11-02 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN211739588U (en) | Air conditioner capable of improving heat exchange performance | |
| CN106546028B (en) | Frostless type refrigerant dual cycle fresh air conditioning unit | |
| CN104061705B (en) | Two-stage Compression air-conditioning system and its control method | |
| CN203231419U (en) | Air conditioner | |
| CN109405102B (en) | Air Conditioning System | |
| CN106016771A (en) | Solar air source heat pump triple co-generation system and control method thereof | |
| CN103411349B (en) | Integration air energy source pump | |
| CN101957061A (en) | Quasi-two-stage compression ultralow temperature air source heat pump water heater with economizer | |
| CN111637659A (en) | High-energy-efficiency heat pump air conditioning system and control method thereof | |
| CN104236155B (en) | Have that coolant is supercool, the defrosting air conditioning system of heat-production functions and control method thereof | |
| CN100439809C (en) | Compensating system and compensating control method for compressor | |
| CN203964436U (en) | Two-stage Compression air-conditioning system | |
| CN102967118A (en) | Refrigerator defrosting control method and refrigerator adopting method | |
| CN203501540U (en) | Integrated air energy heat pump unit | |
| CN202757346U (en) | Central air-conditioning and hot water all-in-one machine | |
| CN106225280A (en) | A kind of refrigeration or heat pump and a kind of Condensing units | |
| CN105333641B (en) | Air-source air conditioning and water heating system | |
| CN108731295B (en) | Heat recovery gas air conditioning system | |
| CN109774418B (en) | Air conditioning system, control method thereof and automobile | |
| CN101957089A (en) | Refrigerating device of air conditioner and household air conditioning system thereof | |
| CN109539620B (en) | Air conditioning system | |
| CN108759157B (en) | One-time throttling two-stage compression heat pump system | |
| CN110966696A (en) | Refrigerant radiation wall integrated air conditioning system with solar jet function and air conditioner | |
| CN209726564U (en) | A kind of phase-change accumulation energy defrosting Multifunctional cold heating system | |
| CN101608852A (en) | Coolant circulating system in the air-conditioner |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |