CN107120861B - heat pump system - Google Patents

heat pump system Download PDF

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Publication number
CN107120861B
CN107120861B CN201710448168.2A CN201710448168A CN107120861B CN 107120861 B CN107120861 B CN 107120861B CN 201710448168 A CN201710448168 A CN 201710448168A CN 107120861 B CN107120861 B CN 107120861B
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Prior art keywords
valve
port
heating
outlet
heat exchanger
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CN201710448168.2A
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CN107120861A (en
Inventor
黄玉优
李欣
叶强蔚
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Gree Electric Appliances Inc of Zhuhai
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Gree Electric Appliances Inc of Zhuhai
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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
    • F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
    • F25B9/08—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using ejectors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B41/00—Fluid-circulation arrangements
    • F25B41/40—Fluid line arrangements
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2341/00—Details of ejectors not being used as compression device; Details of flow restrictors or expansion valves
    • F25B2341/001—Ejectors not being used as compression device
    • F25B2341/0015—Ejectors not being used as compression device using two or more ejectors

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

When the heat pump system is in a heating mode, the second reversing component is connected with the second port of the first heat exchanger, the inlet of the heating ejector, the outlet of the throttling device and the second port of the second heat exchanger; when in the refrigeration mode, the second reversing assembly turns on the second port of the second heat exchanger and the inlet of the refrigeration ejector, the outlet of the throttling device and the second port of the first heat exchanger. The heating ejector and the refrigerating ejector are designed according to the requirements of the heating working condition and the refrigerating working condition respectively, the requirements of the heating working condition and the refrigerating working condition can be met, the heat pump system can switch the heating ejector or the refrigerating ejector to enter circulation according to the working condition through the second reversing component, expansion work can be recovered through the heating ejector and the refrigerating ejector respectively, accordingly, the power of the compressor is reduced, and the energy efficiency of the heat pump system is improved as a whole.

Description

Heat pump system
Technical Field
The application relates to the technical field of temperature regulation, in particular to a heat pump system.
Background
Ejectors are used in a plurality of industries, and the ejectors are used as effective tools for recovering expansion work in refrigeration, so that the compression ratio of a compressor can be reduced, the suction pressure can be increased, and further the power consumption can be reduced. However, since the inlet and outlet directions of the ejector are fixed, the ejector can not work reversely like an electronic throttle device or a capillary tube, and the application of the ejector in a heat pump system is greatly limited.
Patent application CN20090162048. X discloses adding an ejector in a conventional heat pump system to realize multiple circulation control, but the realization of refrigeration and heating is not completely dependent on the ejector, and the application of the ejector mainly comprises high-efficiency application under certain working conditions, rather than full working conditions. Patent application cn201410319864.X discloses that injection refrigeration and normal heating are achieved by means of 1 four-way valve, 4 solenoid valves and 1 one-way valve combination, but that the heating efficiency cannot be improved with the injection cycle. Because the injector product is designed under a fixed working condition, the design parameters of the injector cannot be automatically optimized under the actual use environment so as to adapt to different working condition demands.
Disclosure of Invention
Based on the above, it is necessary to provide a heat pump system aiming at the problem that the fixed working condition design of the ejector in the heat pump system cannot adapt to the requirements of different working conditions.
The application provides a heat pump system, which comprises a compressor, a first heat exchanger, a second heat exchanger, a heating injector, a refrigerating injector, a gas-liquid separator, a throttling device, a first reversing component and a second reversing component, wherein the first reversing component is connected with the first heat exchanger;
the first port of the first heat exchanger is respectively communicated with the exhaust port of the compressor and the injection port of the refrigeration injector through the first reversing component;
the second port of the first heat exchanger is respectively communicated with the outlet of the throttling device and the inlet of the heating injector;
the first port of the second heat exchanger is respectively communicated with the exhaust port of the compressor and the injection port of the heating injector through the first reversing component;
the second port of the second heat exchanger is respectively communicated with the outlet of the throttling device and the inlet of the refrigeration ejector;
the inlet of the gas-liquid separator is respectively communicated with the outlet of the heating ejector and the outlet of the refrigerating ejector, the air outlet of the gas-liquid separator is communicated with the air suction port of the compressor, and the liquid outlet of the gas-liquid separator is communicated with the inlet of the throttling device;
when the heat pump system is in a heating mode, the second reversing component is connected with the second port of the first heat exchanger, the inlet of the heating ejector, the outlet of the throttling device and the second port of the second heat exchanger;
when the heat pump system is in a refrigeration mode, the second reversing assembly is connected with the second port of the second heat exchanger, the inlet of the refrigeration ejector, the outlet of the throttling device and the second port of the first heat exchanger.
In one embodiment, the first reversing assembly includes a first four-way valve, a first heating valve, and a first cooling valve;
the first valve port, the second valve port and the third valve port of the first four-way valve are respectively communicated with the exhaust port of the compressor, the first port of the first heat exchanger and the first port of the second heat exchanger;
the fourth valve port of the first four-way valve is communicated with the injection port of the heating injector through the first heating valve, and the fourth port of the first four-way valve is communicated with the injection port of the refrigerating injector through the first refrigerating valve.
In one embodiment, the first heating valve and the first cooling valve are check valves.
In one embodiment, the second reversing assembly includes a first valve and a second valve,
the first valve is arranged between the second port of the first heat exchanger and the outlet of the throttling device, and the first valve is communicated with the second port of the first heat exchanger and the inlet of the heating injector;
the second valve is arranged between the second port of the second heat exchanger and the outlet of the throttling device, and the second valve is communicated with the second port of the second heat exchanger and the inlet of the refrigeration ejector.
In one embodiment, the first valve and the second valve are check valves.
In one embodiment, the second reversing assembly includes a third valve, a fourth valve, a fifth valve, a sixth valve, a second heating valve, and a second cooling valve,
an inlet of the third valve is communicated with a second port of the first heat exchanger, and an outlet of the third valve is communicated with an inlet of the heating injector through the second heating valve;
an inlet of the fourth valve is communicated with an outlet of the throttling device, and an outlet of the fourth valve is communicated with a second port of the first heat exchanger;
an inlet of the fifth valve is communicated with a second port of the second heat exchanger, and an outlet of the fifth valve is communicated with an inlet of the refrigeration ejector through the second refrigeration valve;
an inlet of the sixth valve is communicated with an outlet of the throttling device, and an outlet of the sixth valve is communicated with the second port of the second heat exchanger.
In one embodiment, the heating system further comprises a third reversing assembly, the outlet of the third valve and the outlet of the fifth valve further being in communication with the inlet of the throttling device via the third reversing assembly.
In one embodiment, a directional valve is arranged between the liquid outlet of the gas-liquid separator and the inlet of the throttling device.
In one embodiment, a heating injection valve is arranged between the outlet of the heating injector and the inlet of the gas-liquid separator;
a refrigeration injection valve is arranged between the outlet of the refrigeration injector and the inlet of the gas-liquid separator.
In one embodiment, the heating injection valve and the cooling injection valve are check valves.
The heat pump system comprises the heating ejector and the refrigerating ejector, the heating ejector and the refrigerating ejector are designed according to the requirements of the heating working condition and the refrigerating working condition respectively, the requirements of the heating working condition and the refrigerating working condition can be met, the heat pump system can switch the heating ejector or the refrigerating ejector to enter circulation according to the working condition through the first reversing component and the second reversing component, expansion work can be recovered through the heating ejector and the refrigerating ejector respectively, the suction pressure of the compressor is improved, the compression ratio of the compressor is reduced, the exhaust temperature of the compressor is reduced, the power of the compressor is reduced, and the energy efficiency of the heat pump system is integrally improved.
Drawings
In order to more clearly illustrate the embodiments of the present application or the technical solutions in the prior art, the drawings required for the embodiments will be briefly described below, and it is apparent that the drawings in the following description are only some embodiments described in the present application, and other drawings may be obtained according to these drawings for a person having ordinary skill in the art.
FIG. 1 is a schematic diagram of a heat pump system according to a first embodiment of the present application;
FIG. 2 is a schematic diagram of a heat pump system according to a second embodiment of the present application;
wherein,
a 100-compressor;
200-a first heat exchanger;
300-a second heat exchanger;
400-heating injector; 410-heating a spray valve;
500 refrigeration ejector; 510-a refrigeration injection valve;
600-gas-liquid separator; 610-directional valve; 620-seventh valve; 700-throttle device;
810-a first four-way valve; 820-a first heating valve; 830-a first refrigeration valve;
910-a first valve; 920-second valve.
1010-a third valve; 1020-fourth valve; 1030-fifth valve; 1040-sixth valve;
1120—a second heating valve; 1130-second refrigeration valve.
Detailed Description
In order to make the objects, technical solutions and advantages of the present application more apparent, the heat pump system of the present application will be further described in detail by way of examples with reference to the accompanying drawings. It should be understood that the specific embodiments described herein are for purposes of illustration only and are not intended to limit the scope of the application.
Referring to fig. 1, the heat pump system of the present application includes a compressor 100, a first heat exchanger 200, a second heat exchanger 300, a heating ejector 400, a cooling ejector 500, a gas-liquid separator 600, a throttling device 700, a first reversing component, and a second reversing component. Wherein, the solid arrow represents the flow direction of the refrigerant during the heating working condition, and the dotted arrow represents the flow direction of the refrigerant during the cooling working condition.
The first port of the first heat exchanger 200 is respectively communicated with the exhaust port of the compressor 100 and the injection port of the refrigeration injector 500 through the first reversing component, and the second port of the first heat exchanger 200 is respectively communicated with the first port of the throttling device 700 and the inlet of the heating injector 400. The first port of the second heat exchanger 300 is respectively communicated with the exhaust port of the compressor 100 and the injection port of the heating ejector 400 through the first reversing component, and the second port of the second heat exchanger 300 is respectively communicated with the first port of the throttling device 700 and the inlet of the refrigerating ejector 500. The inlet of the gas-liquid separator 600 is respectively communicated with the outlet of the heating ejector 400 and the outlet of the refrigerating ejector 500, the outlet of the gas-liquid separator 600 is communicated with the air suction port of the compressor 100, and the liquid outlet of the gas-liquid separator 600 is communicated with the second port of the throttling device 700.
When the heat pump system is in heating mode, the second reversing assembly switches on the second port of the first heat exchanger 200 with the inlet of the heating injector 400 and switches on the outlet of the restriction 700 with the second port of the second heat exchanger 300.
When the heat pump system is in the cooling mode, the second reversing assembly turns on the second port of the second heat exchanger 300 with the inlet of the refrigeration ejector 500 and turns on the outlet of the restriction 700 with the second port of the first heat exchanger 200.
The second reversing component is configured to control on-off of the second port of the first heat exchanger 200 and the outlet of the throttling device 700, the second port of the first heat exchanger 200 and the inlet of the heating injector 400, the second port of the second heat exchanger 300 and the outlet of the throttling device 700, and the second port of the second heat exchanger 300 and the inlet of the refrigerating injector 500, respectively, according to a heating mode or a refrigerating mode.
In the embodiment of the present application, the expansion valve is selected as the throttling device 700. In other embodiments, the throttling device 700 may also be a capillary tube or other component with a throttling function.
In the embodiment of the present application, the first heat exchanger 200 and the second heat exchanger 300 are air-cooled heat exchangers, and in other embodiments, heat exchangers with different structures may be used.
In the embodiment of the application, the ejector is provided with a mixing part and a diffusion part, the inlet and the injection port of the ejector are connected into the mixing part, and the outlet of the ejector is connected into the diffusion part. The high-pressure refrigerant enters the ejector through the inlet, and the low-pressure refrigerant is sucked into the ejector through the injection port, and the high-pressure refrigerant and the low-pressure refrigerant are mixed in the mixing chamber and then are sprayed out through the outlet after the diffusion chamber is decelerated and boosted.
When the heat pump system heats, the refrigerant discharged from the exhaust port of the compressor 100 enters the first heat exchanger 200 through the first reversing component, enters the inlet of the heating ejector 400 through the second reversing component after exchanging heat in the first heat exchanger 200, and then enters the gas-liquid separator 600 through the ejector for gas-liquid separation. The separated gaseous refrigerant enters the compressor 100 through the air suction port of the compressor 100 communicated with the air outlet of the gas-liquid separator 600; the separated liquid refrigerant enters the throttling device 700 through the liquid outlet of the gas-liquid separator 600, then enters the second heat exchanger 300 through the second reversing component, enters the injection port of the heating injector 400 through the first reversing component after the heat exchange of the second heat exchanger 300, and enters the gas-liquid separator 600 after being mixed and pressurized with the refrigerant directly entering the heating injector 400 through the second reversing component after the heat exchange of the first heat exchanger 200, thereby improving the gas pressure of the refrigerant entering the gas-liquid separator 600, improving the suction pressure of the compressor 100, reducing the compression ratio of the compressor 100, reducing the exhaust temperature of the compressor 100, further reducing the power of the compressor 100 and integrally improving the energy efficiency of the heat pump system.
During refrigeration of the heat pump system, the refrigerant discharged from the exhaust port of the compressor 100 enters the second heat exchanger 300 through the first reversing component, enters the inlet of the refrigeration ejector 500 through the second reversing component after heat exchange in the second heat exchanger 300, and then enters the gas-liquid separator 600 through the refrigeration ejector 500 for gas-liquid separation. The separated gaseous refrigerant enters the compressor 100 through the air suction port of the compressor 100 communicated with the air outlet of the gas-liquid separator 600; the separated liquid refrigerant enters the throttling device 700 through the liquid outlet of the gas-liquid separator 600, then enters the first heat exchanger 200 through the second reversing component, enters the injection port of the refrigeration injector 500 through the first reversing component after the heat exchange of the first heat exchanger 200, enters the gas-liquid separator 600 after being mixed and pressurized with the refrigerant directly entering the refrigeration injector 500 through the second reversing component after the heat exchange of the second heat exchanger 300, improves the gas pressure of the refrigerant entering the gas-liquid separator 600, improves the suction pressure of the compressor 100, reduces the compression ratio of the compressor 100, reduces the exhaust temperature of the compressor 100, thereby reducing the power of the compressor 100 and integrally improving the energy efficiency of a heat pump system.
The heating ejector 400 and the refrigerating ejector 500 of the heat pump system are respectively designed according to the requirements of the heating working condition and the refrigerating working condition, can adapt to the requirements of the heating working condition and the refrigerating working condition, and the heat pump system switches the heating ejector 400 or the refrigerating ejector 500 to enter circulation through the first reversing component and the second reversing component according to the working condition, can respectively recover expansion work through the heating ejector 400 and the refrigerating ejector 500, improves the suction pressure of the compressor 100, reduces the compression ratio of the compressor 100, reduces the exhaust temperature of the compressor 100, thereby reducing the power of the compressor 100 and integrally improving the energy efficiency of the heat pump system.
With continued reference to fig. 1, the first reversing component of the heat pump system according to the first embodiment includes a first four-way valve 810, a first heating valve 820, and a first cooling valve 830. The first, second and third ports of the first four-way valve 810 communicate with the discharge port of the compressor 100, the first port of the first heat exchanger 200 and the first port of the second heat exchanger 300, respectively. The fourth port of the first four-way valve 810 is communicated with the injection port of the heating injector 400 through the first heating valve 820, and the fourth port of the first four-way valve 810 is communicated with the injection port of the refrigerating injector 500 through the first refrigerating valve 830.
The fourth port of the first four-way valve 810 is selectively communicated with the injection port of the heating injector 400 and the injection port of the refrigerating injector 500 through the first heating valve 820 and the first refrigerating valve 830, so that the performance parameters of the injector are matched with the working condition of the heat pump.
Optionally, the first heating valve 820 and the first cooling valve 830 are check valves, and the check valves enable the refrigerant to flow unidirectionally from the fourth port of the first four-way valve 810 to the heating injector 400 and the cooling injector 500. The on and off of the one-way valve can be automatically adjusted according to the pressure difference at two ends of the one-way valve, and excessive control is not needed.
Of course, in other embodiments, the first heating valve 820 and the first cooling valve 830 may be other types of valve assemblies, and the on/off of the valve assemblies may be controlled to control whether the refrigerant passes through the valve assemblies.
As an alternative embodiment, the second reversing assembly includes a first valve 910 and a second valve 920. The first valve 910 is disposed between the second port of the first heat exchanger 200 and the outlet of the throttling device 700, and the first valve 910 is in communication with the inlet of the heating injector 400 between the second port of the first heat exchanger 200 and the first valve 910. The second valve 920 is disposed between the second port of the second heat exchanger 300 and the outlet of the throttling device 700, and the second valve 920 is in communication with the inlet of the refrigeration injector 500 between the second valve 920 and the second port of the second heat exchanger 300.
When the heat pump system is in the heating mode, the first valve 910 is turned off, the second valve 920 is turned on, the refrigerant flowing out of the first heat exchanger 200 enters the heating ejector 400, and the refrigerant flowing out of the throttle device 700 enters the second heat exchanger 300.
When the heat pump system is in the cooling mode, the first valve 910 is turned on, the second valve 920 is turned off, the refrigerant flowing out of the second heat exchanger 300 enters the refrigeration ejector 500, and the refrigerant flowing out of the throttle device 700 enters the first heat exchanger 200.
Optionally, the first valve 910 and the second valve 920 are check valves. The inlets of the check valves are all communicated with the outlet of the throttling device 700, and the outlets of the check valves are respectively communicated with the second port of the first heat exchanger 200 and the second port of the second heat exchanger 300, so that the refrigerant flows from the throttling device 700 to the first heat exchanger 200 or the second heat exchanger 300 directionally. Meanwhile, the on and off of the one-way valve can be automatically adjusted according to the pressure difference at two ends of the one-way valve, and excessive control is not needed.
Of course, in other embodiments, the first valve 910 and the first valve 910 may be other types of valve assemblies, and whether the refrigerant passes through the valve assemblies may be controlled by controlling the on-off of the valve assemblies.
As an alternative embodiment, a heating spray valve 410 is provided between the outlet of the heating spray 400 and the inlet of the gas-liquid separator 600, and a cooling spray valve 510 is provided between the outlet of the cooling spray 500 and the inlet of the gas-liquid separator 600.
Optionally, the heating spray valve 410 and the cooling spray valve 510 are check valves. An inlet of the heating spray valve 410 is communicated with an outlet of the heating spray valve 400, and an inlet of the refrigerating spray valve 510 is communicated with an outlet of the refrigerating spray valve 500, so that the refrigerant flows from the heating spray valve 400 to the heating spray valve 410 and from the refrigerating spray valve 500 to the refrigerating spray valve 510 in a directional manner. Meanwhile, the on and off of the one-way valve can be automatically adjusted according to the pressure difference at two ends of the one-way valve, and excessive control is not needed.
Of course, in other embodiments, the heating injection valve 410 and the cooling injection valve 510 may be other types of valve assemblies, and the on/off of the valve assemblies may be controlled to control whether the refrigerant passes through the valve assemblies.
For convenience of description, in the present application, a refrigerant cycle process in which the pressure is increased by the heating ejector 400 or the cooling ejector 500 is referred to as an injection heating cycle, an injection cooling cycle.
The heat pump system of the first embodiment of the application can provide two refrigerant circulation processes, namely injection heating circulation and injection refrigeration circulation, through the first reversing assembly, the second reversing assembly, the heating injector and the refrigeration injector which are communicated with the first reversing assembly and the second reversing assembly.
Injection heating cycle:
including a high pressure refrigerant circuit and a low pressure refrigerant circuit, wherein the first four-way valve 810 is switched to have the first port D in communication with the second port E and the third port C in communication with the fourth port S.
In the high-pressure refrigerant circuit, refrigerant sequentially flows through the discharge port of the compressor 100, the first and second ports D and E of the first four-way valve 810, the first heat exchanger 200, the inlet and outlet of the heating injector 400, the heating injection valve 410, the inlet and outlet of the gas-liquid separator 600, and the suction port of the compressor 100.
In the low-pressure refrigerant circuit, the refrigerant flows through the liquid outlet of the gas-liquid separator 600, the throttling device 700, the second valve 920, the second heat exchanger 300, the third and fourth ports C and S of the first four-way valve 810, the first heating valve 820, the injection port and outlet of the heating injector 400, and the inlet of the gas-liquid separator 600 in order.
Injection refrigeration cycle:
including a high pressure refrigerant circuit and a low pressure refrigerant circuit, wherein the first four-way valve 810 is switched such that the first port D communicates with the third port C and the second port E communicates with the fourth port S.
In the high-pressure refrigerant circuit, refrigerant sequentially flows through the discharge port of the compressor 100, the first and third valve ports D and C of the first four-way valve 810, the second heat exchanger 300, the inlet and outlet of the refrigeration ejector 500, the refrigeration injection valve 510, the inlet and outlet of the gas-liquid separator 600, and the suction port of the compressor 100.
In the low-pressure refrigerant circuit, the refrigerant sequentially flows through the liquid outlet of the gas-liquid separator 600, the throttling device 700, the first valve 910, the first heat exchanger 200, the second and fourth ports E and S of the first four-way valve 810, the first refrigeration valve 830, the injection port and the outlet of the refrigeration injector 500, and the inlet of the gas-liquid separator 600.
In the injection heating cycle and the injection refrigeration cycle, when the first heating valve 820, the first refrigeration valve 830, the first valve 910, the second valve 920, the heating injection valve 410, and the refrigeration injection valve 510 are check valves, the heating and refrigeration switching of the heat pump system only needs to control the first four-way valve 810 in a conventional manner, and the on and off of the check valves can be automatically adjusted according to the pressure difference at two ends of the check valves.
Referring to fig. 2, the heat pump system according to the second embodiment of the present application is different from the heat pump system according to the first embodiment in that the second reversing assembly, the third reversing assembly and the directional valve 610.
In this embodiment, the second reversing assembly includes a third valve 1010, a fourth valve 1020, a fifth valve 1030, a sixth valve 1040, a second heating valve 1120, and a second cooling valve 1130. An inlet of the third valve 1010 communicates with the second port of the first heat exchanger 200, and an outlet of the third valve 1010 communicates with an inlet of the heating injector 400 through the second heating valve 1120; an inlet of the fourth valve 1020 communicates with an outlet of the throttling device 700, and an outlet of the fourth valve 1020 communicates with the second port of the first heat exchanger 200; an inlet of the fifth valve 1030 communicates with the second port of the second heat exchanger 300, and an outlet of the fifth valve 1030 communicates with an inlet of the refrigeration injector 500 through the second refrigeration valve 1130; an inlet of the sixth valve 1040 communicates with an outlet of the restriction 700, and an outlet of the sixth valve 1040 communicates with the second port of the second heat exchanger 300.
By the cooperation of the third valve 1010, the fourth valve 1020, the fifth valve 1030, the sixth valve 1040, the second heating valve 1120, and the second cooling valve 1130, the refrigerant is circulated through the heating injector 400 or through the cooling injector 500, respectively, according to the corresponding working conditions.
For convenience of description, in the present application, a cycle process in which the refrigerant is pressurized by the heating ejector 400 or the cooling ejector 500 is referred to as an injection heating cycle, an injection refrigerating cycle.
As an alternative embodiment, the heating system further comprises a third reversing assembly, through which the outlet of the third valve 1010 and the outlet of the fifth valve 1030 are further in communication with the inlet of the throttling device 700.
That is, the third reversing element can switch the flow direction of the refrigerant passing through the second reversing element, and the refrigerant is increased to avoid the heating and cooling conditions by the heating ejector 400 and the cooling ejector 500. The third reversing component is used for adding the conventional heating cycle and the conventional refrigerating cycle, and converting the heat pump system in the injection heating cycle, the injection refrigerating cycle, the conventional heating cycle and the conventional refrigerating cycle, so that the working condition variety and the regulation range of the heat pump system are increased.
Optionally, the third reversing assembly includes a seventh valve 620, an inlet of the seventh valve 620 being in communication with an outlet of the third valve 1010 and an outlet of the fifth valve 1030, an outlet of the seventh valve 620 being in communication with an inlet of the restriction device 700. For example, the seventh valve 620 may be a solenoid valve. By controlling the on/off state of the seventh valve 620, the refrigerant can be circulated while avoiding the heating ejector 400 and the heating ejector 400.
As an alternative embodiment, a directional valve 610 is disposed between the liquid outlet of the gas-liquid separator 600 and the inlet of the throttling device 700, and the directional valve 610 may be a one-way valve. By providing the directional valve 610, the refrigerant of the third reversing assembly pilot throttle device 700 can be prevented from flowing toward the gas-liquid separator 600. It should be noted that the connection point of the third reversing assembly to the inlet of the throttle device 700 is located between the outlet of the directional valve 610 and the inlet of the throttle device 700.
The heat pump system of the second embodiment of the application also provides the refrigerant circulation process of avoiding the heating injection pump and the refrigeration injection pump through the third reversing assembly, so that four refrigerant circulation processes, namely an injection heating cycle, an injection refrigeration cycle, a conventional heating cycle and a conventional refrigeration cycle, can be provided.
Injection heating cycle:
the four-way valve comprises a high-pressure refrigerant loop and a low-pressure refrigerant loop, wherein the first four-way valve 810 is switched to the state that a first valve port D is communicated with a second valve port E, a third valve port C is communicated with a fourth valve port S, and a third reversing assembly is disconnected; the second refrigeration valve 1130 is opened and the second heating valve 1120 is opened.
In the high-pressure refrigerant circuit, refrigerant flows through the discharge port of the compressor 100, the first and second ports D and E of the first four-way valve 810, the first heat exchanger 200, the third valve 1010, the second heating valve 1120, the inlet and outlet of the heating ejector 400, the heating ejector valve 410, the inlet and outlet of the gas-liquid separator 600, and the suction port of the compressor 100 in this order.
In the low-pressure refrigerant circuit, the refrigerant sequentially flows through the liquid outlet of the gas-liquid separator 600, the directional valve 610, the throttling device 700, the sixth valve 1040, the second heat exchanger 300, the third valve port C and the fourth valve port S of the first four-way valve 810, the first heating valve 820, the inlet and outlet of the heating injector 400, and the inlet of the gas-liquid separator 600.
Injection refrigeration cycle:
including a high pressure refrigerant circuit and a low pressure refrigerant circuit, wherein the first four-way valve 810 is switched to the first port D communicating with the third port C, the second port E communicating with the fourth port S, the third reversing assembly is disconnected, the second refrigeration valve 1130 is opened, and the second heating valve 1120 is disconnected.
In the high-pressure refrigerant circuit, refrigerant flows through the discharge port of the compressor 100, the first and third valve ports D and C of the first four-way valve 810, the second heat exchanger 300, the fifth valve 1030, the second refrigeration valve 1130, the inlet and outlet of the refrigeration ejector 500, the refrigeration injection valve 510, the inlet and outlet of the gas-liquid separator 600, and the suction port of the compressor 100 in this order.
In the low-pressure refrigerant circuit, the refrigerant sequentially flows through a liquid outlet of the gas-liquid separator 600, the directional valve 610, the throttling device 700, the fourth valve 1020, the first heat exchanger 200, the second valve port E and the fourth valve port S of the first four-way valve 810, the first refrigeration valve 830, an injection port and an outlet of the refrigeration injector 500, and an inlet of the gas-liquid separator 600.
Conventional heating cycles:
the first four-way valve 810 is switched to the first port D to communicate with the second port E, the third port C to communicate with the fourth port S, the third reversing assembly is on, the third refrigeration valve 1130 is off, and the second heating valve 1120 is off.
The refrigerant sequentially flows through the discharge port of the compressor 100, the first and second ports D and E of the first four-way valve 810, the first heat exchanger 200, the third valve 1010, the third reversing assembly, the throttling device 700, the sixth valve 1040, the second heat exchanger 300, the third and fourth ports C and S of the first four-way valve 810, the first heating valve 820, the injection port and outlet of the heating injector 400, the heating injection valve 410, and the inlet of the gas-liquid separator 600.
Conventional refrigeration cycle:
the first four-way valve 810 is switched to the first valve port D to communicate with the third valve port C, the second valve port E to communicate with the fourth valve port S, the third reversing assembly is turned on, and the second refrigeration valve 1130 and the second heating valve 1120 are turned off.
The refrigerant sequentially flows through the discharge port of the compressor 100, the first and third ports D and C of the first four-way valve 810, the second heat exchanger 300, the fifth valve 1030, the third reversing assembly, the throttling device 700, the fourth valve 1020, the first heat exchanger 200, the second and fourth ports E and S of the first four-way valve 810, the first refrigerating valve 830, the injection port and outlet of the refrigerating injector 500, the refrigerating injection valve 510, and the inlet of the gas-liquid separator 600.
In the description of the present application, the terms "first," "second," and the like are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
The foregoing examples illustrate only a few embodiments of the application and are described in detail herein without thereby limiting the scope of the application. It should be noted that it will be apparent to those skilled in the art that several variations and modifications can be made without departing from the spirit of the application, which are all within the scope of the application. Accordingly, the scope of protection of the present application is to be determined by the appended claims.

Claims (7)

1. A heat pump system characterized by comprising a compressor (100), a first heat exchanger (200), a second heat exchanger (300), a heating ejector (400), a refrigeration ejector (500), a gas-liquid separator (600), a throttling device (700), a first reversing assembly and a second reversing assembly;
the first port of the first heat exchanger (200) is respectively communicated with the exhaust port of the compressor (100) and the injection port of the refrigeration injector (500) through the first reversing component;
the second port of the first heat exchanger (200) is respectively communicated with the outlet of the throttling device (700) and the inlet of the heating ejector (400);
the first port of the second heat exchanger (300) is respectively communicated with the exhaust port of the compressor (100) and the injection port of the heating injector (400) through the first reversing component;
a second port of the second heat exchanger (300) is respectively communicated with an outlet of the throttling device (700) and an inlet of the refrigeration ejector (500);
the inlet of the gas-liquid separator (600) is respectively communicated with the outlet of the heating ejector (400) and the outlet of the refrigerating ejector (500), the air outlet of the gas-liquid separator (600) is communicated with the air suction port of the compressor (100), and the liquid outlet of the gas-liquid separator (600) is communicated with the inlet of the throttling device (700);
when the heat pump system is in a heating mode, the second reversing assembly is connected with the second port of the first heat exchanger (200) and the inlet of the heating ejector (400), the outlet of the throttling device (700) and the second port of the second heat exchanger (300);
when the heat pump system is in a refrigeration mode, the second reversing assembly switches on the second port of the second heat exchanger (300) and the inlet of the refrigeration ejector (500), the outlet of the throttling device (700) and the second port of the first heat exchanger (200);
the second reversing component comprises a third valve (1010), a fifth valve (1030), a second heating valve (1120) and a second refrigerating valve (1130), wherein an inlet of the third valve (1010) is communicated with a second port of the first heat exchanger (200), and an outlet of the third valve (1010) is communicated with an inlet of the heating injector (400) through the second heating valve (1120);
an inlet of the fifth valve (1030) is communicated with a second port of the second heat exchanger (300), and an outlet of the fifth valve (1030) is communicated with an inlet of the refrigeration injector (500) through the second refrigeration valve (1130);
the heat pump system further comprises a third reversing assembly, through which the outlet of the third valve (1010) and the outlet of the fifth valve (1030) are also in communication with the inlet of the throttling device (700).
2. The heat pump system of claim 1, wherein the first reversing assembly comprises a first four-way valve (810), a first heating valve (820), and a first cooling valve (830);
the first valve port, the second valve port and the third valve port of the first four-way valve (810) are respectively communicated with the exhaust port of the compressor (100), the first port of the first heat exchanger (200) and the first port of the second heat exchanger (300);
the fourth valve port of the first four-way valve (810) is communicated with the injection port of the heating injector (400) through the first heating valve (820), and the fourth port of the first four-way valve (810) is communicated with the injection port of the refrigerating injector (500) through the first refrigerating valve (830).
3. The heat pump system of claim 2, wherein the first heating valve (820) and the first cooling valve (830) are check valves.
4. The heat pump system of claim 1, wherein the second reversing assembly further comprises a fourth valve (1020) and a sixth valve (1040);
an inlet of the fourth valve (1020) communicates with an outlet of the throttling device (700), an outlet of the fourth valve (1020) communicates with a second port of the first heat exchanger (200);
an inlet of the sixth valve (1040) communicates with an outlet of the restriction (700), and an outlet of the sixth valve (1040) communicates with a second port of the second heat exchanger (300).
5. The heat pump system according to claim 4, characterized in that a directional valve (610) is provided between the liquid outlet of the gas-liquid separator (600) and the inlet of the throttling device (700).
6. The heat pump system according to claim 1, wherein a heating injection valve (410) is provided between the outlet of the heating injector (400) and the inlet of the gas-liquid separator (600);
a refrigeration injection valve (510) is arranged between the outlet of the refrigeration injector (500) and the inlet of the gas-liquid separator (600).
7. The heat pump system of claim 6, wherein the heating injection valve (410) and the cooling injection valve (510) are check valves.
CN201710448168.2A 2017-06-14 2017-06-14 heat pump system Active CN107120861B (en)

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CN107796146B (en) * 2017-10-20 2023-12-15 珠海格力电器股份有限公司 Condensing system, air conditioning system and control method
CN108224838A (en) * 2017-12-27 2018-06-29 青岛海尔空调电子有限公司 Air-conditioner system
CN109579343A (en) * 2018-10-29 2019-04-05 青岛海尔（胶州）空调器有限公司 Air conditioner and its control method
CN109515115B (en) * 2018-11-27 2021-05-25 上海交通大学 Automobile air conditioning system using carbon dioxide as working medium and control method
CN116241962A (en) * 2023-03-29 2023-06-09 珠海格力电器股份有限公司 Air conditioning system, air conditioning unit and control method

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