CN110500804B - Heat pump system and control method - Google Patents
Heat pump system and control method Download PDFInfo
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- CN110500804B CN110500804B CN201910865542.8A CN201910865542A CN110500804B CN 110500804 B CN110500804 B CN 110500804B CN 201910865542 A CN201910865542 A CN 201910865542A CN 110500804 B CN110500804 B CN 110500804B
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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
- F25B13/00—Compression machines, plants or systems, with reversible cycle
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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
- F25B31/00—Compressor arrangements
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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
- F25B41/00—Fluid-circulation arrangements
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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
- F25B41/00—Fluid-circulation arrangements
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
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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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02741—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using one four-way valve
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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
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/029—Control issues
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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
The invention provides a heat pump system and a control method. The heat pump system comprises a compressor, a four-way valve, an indoor heat exchanger, a first throttling element and a first heat source heat exchanger which are sequentially connected to form a main cycle of a refrigerating and heating refrigerant, and further comprises a second heat source heat exchanger and a second throttling element which are sequentially connected to form an auxiliary heat exchange branch, wherein one end of the second throttling element is connected to a pipeline between the indoor heat exchanger and the first heat source heat exchanger, the other end of the second throttling element is connected with one end of the second heat source heat exchanger, and the other end of the second heat source heat exchanger is connected to an air suction port of the compressor. The heat pump system and the control method thereof ensure that the heat pump system is provided with two evaporators no matter in a heating working mode or a refrigerating working mode, so that the heat pump system can use two heat sources simultaneously, the operation energy efficiency of the heat pump system is greatly improved, and the operation cost of the heat pump system is reduced.
Description
Technical Field
The invention belongs to the technical field of air conditioning, and particularly relates to a heat pump system and a control method.
Background
In recent years, with the increase of environmental pollution and the exhaustion of energy sources, there is a need to continuously promote air conditioning technology, and the goal of efficient operation of air conditioners is achieved by adopting efficient energy-saving technical means such as (temperature and humidity independent control technology and heat pump technology). For the foregoing reasons, various heat pump systems with dual evaporators have been developed in the market, but most of these heat pump systems have the purpose of cooling by evaporation and heat absorption of the dual evaporators, so that the refrigerant circulation system is strictly limited to a cooling mode or a heating mode, that is, the existing heat pump systems have the problem of single function, and there are few heat pump systems in which the refrigerant circulation has the switching working conditions of heating and cooling, but the dual evaporators only have the function of the dual evaporators in the heating mode or the cooling mode, so that the load distribution of the two evaporators cannot be flexibly adjusted, and the energy efficiency of the heat pump system is relatively low. For example, patent publication No. CN205505465U discloses a single-machine two-stage compression double-evaporator large-temperature-difference water chilling unit, which can only realize double-evaporation-temperature refrigeration, has a single function, cannot flexibly control loads of two evaporation sides, does not have a mode of heating working conditions, and is idle in winter, thereby wasting resources.
Disclosure of Invention
Therefore, the technical problem to be solved by the invention is to provide the heat pump system and the control method, so that the heat pump system is provided with two evaporators no matter in a heating working mode or a refrigerating working mode, the heat pump system can be ensured to simultaneously utilize two heat sources, the operation energy efficiency of the heat pump system is greatly improved, and the operation cost of the heat pump system is reduced.
In order to solve the problems, the invention provides a heat pump system, which comprises a compressor, a four-way valve, an indoor heat exchanger, a first throttling element and a first heat source heat exchanger which are sequentially connected to form a main cycle of a refrigerating and heating refrigerant, and also comprises a second heat source heat exchanger and a second throttling element which are sequentially connected to form an auxiliary heat exchange branch, wherein one end of the second throttling element is connected to a pipeline between the indoor heat exchanger and the first heat source heat exchanger, the other end of the second throttling element is connected with one end of the second heat source heat exchanger, and the other end of the second heat source heat exchanger is connected to an air suction port of the compressor.
Preferably, the second heat source heat exchanger has an evaporation temperature higher than that of the first heat source heat exchanger or the indoor heat exchanger when it is used as an evaporator.
Preferably, the compressor comprises a first double-stage compressor and a second double-stage compressor which are connected in parallel, the exhaust port of the first double-stage compressor and the exhaust port of the second double-stage compressor are integrated to form a first pipeline and are connected with an A port of the four-way valve, and the air suction port of the first double-stage compressor and the air suction port of the second double-stage compressor are integrated to form a second pipeline and are connected with a C port of the four-way valve.
Preferably, the first two-stage compressor and the second two-stage compressor are both air-supplementing enthalpy-increasing compressors, and further comprise a flash device and a third throttling element, wherein the flash device and the third throttling element are sequentially connected between the first throttling element and the first heat source heat exchanger, the flash device is positioned between the first throttling element and the third throttling element, the first two-stage compressor is provided with a first air supplementing port, the second two-stage compressor is provided with a second air supplementing port, an air supplementing branch of the flash device is connected with the first air supplementing port through a first electromagnetic valve, and an air supplementing branch of the flash device is connected with the second air supplementing port through a second electromagnetic valve.
Preferably, the auxiliary heat exchange branch comprises a first switching pipeline and a second switching pipeline, a first trunk section is arranged between the indoor heat exchanger and the first throttling element, a second trunk section is arranged between the third throttling element and the first heat source heat exchanger, a third electromagnetic valve is arranged in the first switching pipeline and is arranged between the second throttling element and the first trunk section, and a fourth electromagnetic valve is arranged in the second switching pipeline and is arranged between the second throttling element and the second trunk section.
Preferably, the auxiliary heat exchange branch further comprises a fifth electromagnetic valve connected between the second heat source heat exchanger and the suction port of the compressor.
Preferably, the second pipeline is provided with a first branch section connected with the first two-stage compressor and a second branch section connected with the second two-stage compressor, and a sixth electromagnetic valve is further arranged on the second branch section.
The invention also provides a control method of the heat pump system, which comprises the following steps:
acquiring a working mode of a heat pump system;
and controlling the on-off of the electromagnetic valve and the throttling element so as to enable the heat pump system to operate in the acquired working mode.
Preferably, the method comprises the steps of,
when the obtained working mode is a double-heat-source air supplementing heating mode, controlling the port A and the port D and the port B and the port C of the four-way valve to be respectively communicated, controlling the first throttling element, the second throttling element, the third throttling element, the first electromagnetic valve, the third electromagnetic valve and the fifth electromagnetic valve to be opened, and controlling the second electromagnetic valve, the fourth electromagnetic valve and the sixth electromagnetic valve to be closed;
or when the obtained working mode is a double-heat source non-air supplementing heating mode, controlling the port A and the port D and the port B and the port C of the four-way valve to be respectively communicated, controlling the first throttling element, the second throttling element, the third electromagnetic valve and the fifth electromagnetic valve to be opened, and controlling the first electromagnetic valve, the second electromagnetic valve, the fourth electromagnetic valve and the sixth electromagnetic valve to be closed;
or when the obtained working mode is a single heat source air supplementing heating mode, controlling the port A and the port D and the port B and the port C of the four-way valve to be respectively communicated, controlling the first throttling element, the third throttling element, the first electromagnetic valve, the second electromagnetic valve and the sixth electromagnetic valve to be opened, and controlling the third electromagnetic valve, the fourth electromagnetic valve, the fifth electromagnetic valve and the second throttling element to be closed;
or when the obtained working mode is a single-heat source non-air supplementing heating mode, controlling the port A and the port D and the port B and the port C of the four-way valve to be respectively communicated, controlling the first throttling element, the third electromagnetic valve and the sixth electromagnetic valve to be opened, and controlling the first electromagnetic valve, the second electromagnetic valve, the third electromagnetic valve, the fourth electromagnetic valve, the fifth electromagnetic valve and the second throttling element to be closed.
Preferably, the method comprises the steps of,
when the obtained working mode is a double-heat-source air-supplementing refrigeration mode, controlling the port A and the port B and the port C and the port D of the four-way valve to be respectively communicated, controlling the first throttling element, the second throttling element, the third throttling element, the first electromagnetic valve, the fourth electromagnetic valve and the fifth electromagnetic valve to be opened, and controlling the second electromagnetic valve, the third electromagnetic valve and the sixth electromagnetic valve to be closed;
or when the obtained working mode is a double-heat-source non-air-supplementing refrigeration mode, controlling the port A and the port B and the port C and the port D of the four-way valve to be respectively communicated, controlling the first throttling element, the second throttling element, the third throttling element, the fourth electromagnetic valve and the fifth electromagnetic valve to be opened, and controlling the first electromagnetic valve, the second electromagnetic valve, the third electromagnetic valve and the sixth electromagnetic valve to be closed;
or when the acquired working mode is a single heat source air supplementing and refrigerating mode, controlling the port A and the port B and the port C and the port D of the four-way valve to be respectively communicated, controlling the first throttling element, the third throttling element, the first electromagnetic valve, the second electromagnetic valve and the sixth electromagnetic valve to be opened, and controlling the second throttling element, the third electromagnetic valve, the fourth electromagnetic valve and the fifth electromagnetic valve to be closed;
or when the obtained working mode is a single-heat-source non-air-supplementing refrigeration mode, controlling the port A and the port B and the port C and the port D of the four-way valve to be respectively communicated, controlling the first throttling element, the third throttling element and the sixth electromagnetic valve to be opened, and controlling the second throttling element, the first electromagnetic valve, the second electromagnetic valve, the third electromagnetic valve, the fourth electromagnetic valve and the fifth electromagnetic valve to be closed.
Preferably, the method comprises the steps of,
when the acquired working mode is a defrosting mode, an A port and a B port of the four-way valve are controlled to be communicated, the second throttling element and the fifth electromagnetic valve are controlled to be opened, and the first throttling element, the third throttling element, the first electromagnetic valve, the second electromagnetic valve, the third electromagnetic valve, the fourth electromagnetic valve and the sixth electromagnetic valve are controlled to be closed.
According to the heat pump system and the control method, the auxiliary heat exchange branch is connected between the pipeline between the indoor heat exchanger and the first heat source heat exchanger and the air suction port of the compressor, so that the heat pump system is in a refrigerating mode or a heating mode, and the second heat source heat exchanger plays a role in heat absorption and evaporation, so that a double-evaporation temperature mode of the heat pump system under all working conditions is realized, the refrigerating and heating requirements are met at the same time, the operation energy efficiency of the heat pump system is improved, the operation cost is reduced, and the system can be suitable for occasions with independent temperature and humidity control.
Drawings
FIG. 1 is a schematic diagram of a heat pump system according to an embodiment of the present invention;
FIG. 2 is a schematic diagram illustrating a refrigerant flow direction when the heat pump system shown in FIG. 1 is operated in a dual heat source air-supplementing heating mode;
FIG. 3 is a schematic diagram illustrating a refrigerant flow direction when the heat pump system shown in FIG. 1 is operated in a dual heat source non-air-supplementing heating mode;
FIG. 4 is a schematic diagram illustrating a refrigerant flow direction when the heat pump system shown in FIG. 1 is operated in a single heat source air-supplementing heating mode;
FIG. 5 is a schematic diagram illustrating a refrigerant flow direction when the heat pump system shown in FIG. 1 is operated in a single heat source non-air-supplementing heating mode;
FIG. 6 is a schematic diagram illustrating a refrigerant flow direction when the heat pump system of FIG. 1 is in a defrost mode;
FIG. 7 is a schematic diagram illustrating a refrigerant flow direction when the heat pump system of FIG. 1 is in a dual heat source air-supplementing refrigeration mode;
FIG. 8 is a schematic diagram illustrating a refrigerant flow direction when the heat pump system of FIG. 1 is in a dual heat source non-supplemental cooling mode;
FIG. 9 is a schematic diagram illustrating a refrigerant flow direction when the heat pump system of FIG. 1 is in a single heat source air-supplementing refrigeration mode;
fig. 10 is a schematic diagram of the refrigerant flow direction when the heat pump system shown in fig. 1 is operated in the single heat source non-air-supplementing heating mode.
The reference numerals are expressed as:
111. a first two-stage compressor; 112. a second two-stage compressor; 12. a four-way valve; 13. an indoor heat exchanger; 14. a first throttling element; 15. a first heat source heat exchanger; 16. a flash; 17. a third throttling element; 21. a second heat source heat exchanger; 22. a second throttling element; 101. a first electromagnetic valve; 102. a second electromagnetic valve; 103. a third electromagnetic valve; 104. a fourth electromagnetic valve; 105. a fifth electromagnetic valve; 106. a sixth electromagnetic valve; 201. a first switching pipeline; 202. a second switching pipeline; 203. a first trunk section; 204. a second trunk section; 205. a first road section; 206. and a second road section.
Detailed Description
Referring to fig. 1 to 10, according to an embodiment of the present invention, there is provided a heat pump system including a compressor, a four-way valve 12, an indoor heat exchanger 13, a first throttling element 14, and a first heat source heat exchanger 15 sequentially connected to form a main cycle of a cooling/heating refrigerant, and further including a second heat source heat exchanger 21 and a second throttling element 22 sequentially connected to form an auxiliary heat exchange branch, wherein one end of the second throttling element 22 is connected to a pipeline between the indoor heat exchanger 13 and the first heat source heat exchanger 15, the other end of the second throttling element 22 is connected to one end of the second heat source heat exchanger 21, and the other end of the second heat source heat exchanger 21 is connected to an air inlet of the compressor. In this technical scheme, because the auxiliary heat exchange branch is connected between the indoor heat exchanger 13 and the pipeline between the first heat source heat exchanger 15 and the air suction port of the compressor, this makes the heat pump system be in either a refrigeration mode or a heating mode, the second heat source heat exchanger 21 will exert the effect of endothermic evaporation, so the dual evaporation temperature mode under the full operating mode of the heat pump system is realized, while simultaneously meeting the refrigeration and heating demands, the operation energy efficiency of the heat pump system is improved, the operation cost is reduced, and the system can be suitable for the occasion of independent temperature and humidity control.
Preferably, the evaporation temperature of the second heat source heat exchanger 21 is higher than that when the evaporator is used in the first heat source heat exchanger 15 or the indoor heat exchanger 13. Specifically, the first heat source heat exchanger 15 may be a conventional heat exchanger with forced convection (i.e. an air source), while the second heat source heat exchanger 21 may be a heat exchanger with solar energy and a water source (including river and lake water), for example, in winter (when the outside air temperature is low), the second heat source heat exchanger 21 uses a solar heat exchanger to recover the heat of a high-temperature heat source (through a corresponding working medium) and then exchange heat with the refrigerant in the main cycle of the cooling and heating refrigerant, so as to raise the evaporation temperature flowing through the second heat source heat exchanger 21, which will definitely improve the energy efficiency of the compressor, that is, improve the energy efficiency of the heat pump system.
To further enhance the energy efficiency of the heat pump system, the compressor preferably includes a first dual-stage compressor 111 and a second dual-stage compressor 112 connected in parallel, the four-way valve 12 has an a port, a B port, a C port, and a D port (as is well known in the art, the four-way valve has 4 ports, which are only specifically defined herein for convenience of description and are not unduly limiting the present invention), the exhaust port of the first dual-stage compressor 111 and the exhaust port of the second dual-stage compressor 112 are combined to form a first pipeline and connected to the a port of the four-way valve 12, and the intake port of the first dual-stage compressor 111 and the intake port of the second dual-stage compressor 112 are combined to form a second pipeline and connected to the C port of the four-way valve 12.
Further, the first two-stage compressor 111 and the second two-stage compressor 112 are both vapor-filling enthalpy-increasing compressors, and further include a flash evaporator 16 and a third throttling element 17, the flash evaporator 16 and the third throttling element 17 are sequentially connected between the first throttling element 14 and the first heat source heat exchanger 15, the flash evaporator 16 is located between the first throttling element 14 and the third throttling element 17, the first two-stage compressor 111 has a first vapor-filling port, the second two-stage compressor 112 has a second vapor-filling port, the vapor-filling branch of the flash evaporator 16 is connected with the first vapor-filling port through a first electromagnetic valve 101, the vapor-filling branch of the flash evaporator 16 is connected with the second vapor-filling port through a second electromagnetic valve 102, and the heat pump system is designed to have a corresponding vapor-filling enthalpy-filling system, so that the energy efficiency of the system can be further improved, wherein the first electromagnetic valve 101 and the second electromagnetic valve 102 are designed to be favorable for meeting the flow path switching requirements of the heat pump system under different working modes.
The auxiliary heat exchange branch comprises a first switching pipeline 201 and a second switching pipeline 202, a first trunk section 203 is arranged between the indoor heat exchanger 13 and the first throttling element 14, a second trunk section 204 is arranged between the third throttling element 17 and the first heat source heat exchanger 15, a third electromagnetic valve 103 is arranged in the first switching pipeline 201 and is arranged between the second throttling element 22 and the first trunk section 203, a fourth electromagnetic valve 104 is arranged in the second switching pipeline 202 and is arranged between the second throttling element 22 and the second trunk section 204, and therefore the flow path of a refrigerant in the heat pump system can be further enriched through the design of the third electromagnetic valve 103 and the fourth electromagnetic valve 104, and the type of the working mode of the heat pump system is further enriched. Also, further, the auxiliary heat exchange branch further includes a fifth electromagnetic valve 105, and the fifth electromagnetic valve 105 is connected between the second heat source heat exchanger 21 and the air suction port of the compressor; the second pipeline has a first branch section 205 connected to the first two-stage compressor 111 and a second branch section 206 connected to the second two-stage compressor 112, and the second branch section 206 is further provided with a sixth electromagnetic valve 106.
According to an embodiment of the present invention, there is also provided a control method of a heat pump system, including the steps of:
acquiring a working mode of a heat pump system;
and controlling the on-off of the electromagnetic valve and the throttling element so as to enable the heat pump system to operate in the acquired working mode.
The operation modes can be, for example, nine modes of a double-heat-source air-supplementing heating mode, a double-heat-source non-air-supplementing heating mode, a single-heat-source non-air-supplementing heating mode, a defrosting mode, a double-heat-source air-supplementing cooling mode, a double-heat-source non-air-supplementing cooling mode, a single-heat-source air-supplementing cooling mode and a single-heat-source non-air-supplementing cooling mode.
For example, as shown in fig. 2 to 5, when the obtained operation mode is the dual-heat-source air-supplementing heating mode, the port a and the port D and the port B and the port C of the four-way valve 12 are controlled to be respectively communicated, the first throttling element 14, the second throttling element 22, the third throttling element 17, the first electromagnetic valve 101, the third electromagnetic valve 103 and the fifth electromagnetic valve 105 are controlled to be opened, and the second electromagnetic valve 102, the fourth electromagnetic valve 104 and the sixth electromagnetic valve 106 are controlled to be closed; or when the obtained working mode is a dual-heat source non-air supplementing heating mode, controlling the port A and the port D of the four-way valve 12 and the port B and the port C to be respectively communicated, controlling the first throttling element 14, the second throttling element 22, the third throttling element 17, the third electromagnetic valve 103 and the fifth electromagnetic valve 105 to be opened, and controlling the first electromagnetic valve 101, the second electromagnetic valve 102, the fourth electromagnetic valve 104 and the sixth electromagnetic valve 106 to be closed; or when the obtained working mode is a single-heat-source air supplementing heating mode, controlling the port A and the port D of the four-way valve 12 and the port B and the port C to be respectively communicated, controlling the first throttling element 14, the third throttling element 17, the first electromagnetic valve 101, the second electromagnetic valve 102 and the sixth electromagnetic valve 106 to be opened, and controlling the third electromagnetic valve 103, the fourth electromagnetic valve 104, the fifth electromagnetic valve 105 and the second throttling element 22 to be closed; or when the obtained working mode is a single-heat-source non-air-supplementing heating mode, the port A and the port D of the four-way valve 12 and the port B and the port C of the four-way valve 12 are respectively communicated, the first throttling element 14, the third throttling element 17, the third solenoid valve 103 and the sixth solenoid valve 106 are controlled to be opened, and the first solenoid valve 101, the second solenoid valve 102, the third solenoid valve 103, the fourth solenoid valve 104, the fifth solenoid valve 105 and the second throttling element 22 are controlled to be closed. In this technical solution, it should be emphasized that, when the working mode adopts a dual heat source (whether refrigeration or heating), the sixth electromagnetic valve 106 should be ensured to be disconnected, so that the refrigerant in the main cycle of the refrigeration and heating refrigerant and the refrigerant in the auxiliary heat exchange branch independently enter the first two-stage compressor 111 and the second two-stage compressor 112 respectively, and the energy efficiency of the heat pump system is prevented from being reduced after the two refrigerants with different temperatures are mixed; in the case of a single heat source, the sixth electromagnetic valve 106 is ensured to be opened and the fifth electromagnetic valve 105 is ensured to be closed, so that the suction ports of the low-pressure stage compression chambers of the first and second two-stage compressors 111 and 112 share a refrigerant pressure. It will be further appreciated that in the dual heat source heating mode (air-make-up or non-air-make-up), both the second heat source heat exchanger 21 and the first heat source heat exchanger 15 are used as evaporators, while the indoor heat exchanger 13 is used as a condenser.
For another example, as shown in fig. 7 to 10, when the obtained operation mode is the dual heat source air-supplementing refrigeration mode, the port a and the port B, and the port C and the port D of the four-way valve 12 are controlled to be respectively communicated, the first throttling element 14, the second throttling element 22, the third throttling element 17, the first electromagnetic valve 101, the fourth electromagnetic valve 104, and the fifth electromagnetic valve 105 are controlled to be opened, and the second electromagnetic valve 102, the third electromagnetic valve 103, and the sixth electromagnetic valve 106 are controlled to be closed; or when the obtained working mode is a double-heat-source non-air-supplementing refrigeration mode, controlling the port A and the port B and the port C and the port D of the four-way valve 12 to be respectively communicated, controlling the first throttling element 14, the second throttling element 22, the third throttling element 17, the fourth electromagnetic valve 104 and the fifth electromagnetic valve 105 to be opened, and controlling the first electromagnetic valve 101, the second electromagnetic valve 102, the third electromagnetic valve 103 and the sixth electromagnetic valve 106 to be closed; or when the obtained working mode is a single heat source air supplementing and refrigerating mode, controlling the port A and the port B and the port C and the port D of the four-way valve 12 to be respectively communicated, controlling the first throttling element 14, the third throttling element 17, the first electromagnetic valve 101, the second electromagnetic valve 102 and the sixth electromagnetic valve 106 to be opened, and controlling the second throttling element 22, the third electromagnetic valve 103, the fourth electromagnetic valve 104 and the fifth electromagnetic valve 105 to be closed; or when the obtained working mode is a single-heat-source non-air-supplementing refrigeration mode, controlling the port A and the port B of the four-way valve 12 and the port C and the port D to be respectively communicated, controlling the first throttling element 14, the third throttling element 17 and the sixth electromagnetic valve 106 to be opened, and controlling the second throttling element 22, the first electromagnetic valve 101, the second electromagnetic valve 102, the third electromagnetic valve 103, the fourth electromagnetic valve 104 and the fifth electromagnetic valve 105 to be closed. It will be further appreciated that in the dual heat source cooling mode (either with or without air charge), both the second heat source heat exchanger 21 and the indoor heat exchanger 13 function as evaporators, while the first heat source heat exchanger 15 functions as a condenser.
Specifically, as shown in fig. 6, when the obtained operation mode is the defrosting mode, the port a and the port B of the four-way valve 12 are controlled to be communicated, the second throttling element 22 and the fifth electromagnetic valve 105 are controlled to be opened, the first throttling element 14, the third throttling element 17, the first electromagnetic valve 101, the second electromagnetic valve 102, the third electromagnetic valve 103, the fourth electromagnetic valve 104 and the sixth electromagnetic valve 106 are controlled to be closed, and at this time, the second heat source heat exchanger 21 utilizes the heat of the external high-temperature heat source to defrost the first heat source heat exchanger 15, so that the indoor temperature cannot be greatly fluctuated.
It will be readily appreciated by those skilled in the art that the above advantageous ways can be freely combined and superimposed without conflict.
The foregoing description of the preferred embodiments of the invention is not intended to be limiting, but rather is intended to cover all modifications, equivalents, and alternatives falling within the spirit and principles of the invention. The foregoing is merely a preferred embodiment of the present invention, and it should be noted that it will be apparent to those skilled in the art that modifications and variations can be made without departing from the technical principles of the present invention, and these modifications and variations should also be regarded as the scope of the invention.
Claims (8)
1. The heat pump system is characterized by comprising a compressor, a four-way valve (12), an indoor heat exchanger (13), a first throttling element (14) and a first heat source heat exchanger (15) which are sequentially connected to form a main cycle of a refrigerating and heating refrigerant, and further comprising a second heat source heat exchanger (21) and a second throttling element (22) which are sequentially connected to form an auxiliary heat exchange branch, wherein one end of the second throttling element (22) is connected to a pipeline between the indoor heat exchanger (13) and the first heat source heat exchanger (15), the other end of the second throttling element (22) is connected with one end of the second heat source heat exchanger (21), and the other end of the second heat source heat exchanger (21) is connected to an air suction port of the compressor; the compressor comprises a first double-stage compressor (111) and a second double-stage compressor (112) which are connected in parallel, wherein an exhaust port of the first double-stage compressor (111) and an exhaust port of the second double-stage compressor (112) are combined to form a first pipeline and are connected with an A port of the four-way valve (2), and an air suction port of the first double-stage compressor (111) and an air suction port of the second double-stage compressor (112) are combined to form a second pipeline and are connected with a C port of the four-way valve (12); the first two-stage compressor (111) and the second two-stage compressor (112) are both air supplementing enthalpy increasing compressors, the air supplementing enthalpy increasing compressors further comprise a flash evaporator (16) and a third throttling element (17), the flash evaporator (16) and the third throttling element (17) are sequentially connected between the first throttling element (14) and the first heat source heat exchanger (15), the flash evaporator (16) is positioned between the first throttling element (14) and the third throttling element (17), the first two-stage compressor (111) is provided with a first air supplementing port, the second two-stage compressor (112) is provided with a second air supplementing port, the air supplementing branch of the flash evaporator (16) is connected with the first air supplementing port through a first electromagnetic valve (101), and the air supplementing branch of the flash evaporator (16) is connected with the second air supplementing port through a second electromagnetic valve (102); the auxiliary heat exchange branch comprises a first switching pipeline (201) and a second switching pipeline (202), a first dry section (203) is arranged between the indoor heat exchanger (13) and the first throttling element (14), a second dry section (204) is arranged between the third throttling element (17) and the first heat source heat exchanger (15), a third electromagnetic valve (103) is arranged in the first switching pipeline (201) and is arranged between the second throttling element (22) and the first dry section (203), and a fourth electromagnetic valve (104) is arranged in the second switching pipeline (202) and is arranged between the second throttling element (22) and the second dry section (204).
2. The heat pump system according to claim 1, characterized in that the evaporation temperature of the second heat source heat exchanger (21) is higher than the evaporation temperature when the evaporator is in the first heat source heat exchanger (15) or the indoor heat exchanger (13).
3. The heat pump system according to claim 1, wherein the auxiliary heat exchange branch further comprises a fifth solenoid valve (105), the fifth solenoid valve (105) being connected between the second heat source heat exchanger (21) and the suction port of the compressor.
4. A heat pump system according to claim 3, wherein the second pipeline has a first branch section (205) connected to the first two-stage compressor (111) and a second branch section (206) connected to the second two-stage compressor (112), and wherein a sixth solenoid valve (106) is further provided on the second branch section (206).
5. A control method of a heat pump system according to any one of claims 1 to 4, comprising the steps of:
acquiring a working mode of a heat pump system;
and controlling the on-off of the electromagnetic valve and the throttling element so as to enable the heat pump system to operate in the acquired working mode.
6. The control method according to claim 5, wherein,
when the obtained working mode is a double-heat-source air supplementing heating mode, controlling the port A and the port D of the four-way valve 12 and the port B and the port C to be respectively communicated, controlling the first throttling element (14), the second throttling element (22), the third throttling element (17), the first electromagnetic valve (101), the third electromagnetic valve (103) and the fifth electromagnetic valve (105) to be opened, and controlling the second electromagnetic valve (102), the fourth electromagnetic valve (104) and the sixth electromagnetic valve (106) to be closed;
or when the obtained working mode is a double-heat source non-air supplementing heating mode, controlling the port A and the port D of the four-way valve 12 and the port B and the port C to be respectively communicated, controlling the first throttling element (14), the second throttling element (22), the third throttling element (17), the third electromagnetic valve (103) and the fifth electromagnetic valve (105) to be opened, and controlling the first electromagnetic valve (101), the second electromagnetic valve (102), the fourth electromagnetic valve (104) and the sixth electromagnetic valve (106) to be closed;
or when the obtained working mode is a single heat source air supplementing heating mode, controlling the port A and the port D of the four-way valve 12 and the port B and the port C to be respectively communicated, controlling the first throttling element (14), the third throttling element (17), the first electromagnetic valve (101), the second electromagnetic valve (102) and the sixth electromagnetic valve (106) to be opened, and controlling the third electromagnetic valve (103), the fourth electromagnetic valve (104), the fifth electromagnetic valve (105) and the second throttling element (22) to be closed;
or when the obtained working mode is a single-heat source non-air supplementing heating mode, controlling the port A and the port D of the four-way valve 12 and the port B and the port C to be respectively communicated, controlling the first throttling element (14), the third throttling element (17), the third solenoid valve (103) and the sixth solenoid valve (106) to be opened, and controlling the first solenoid valve (101), the second solenoid valve (102), the third solenoid valve (103), the fourth solenoid valve (104), the fifth solenoid valve (105) and the second throttling element (22) to be closed.
7. The control method according to claim 5, wherein,
when the obtained working mode is a double-heat-source air-supplementing refrigeration mode, controlling the port A and the port B and the port C and the port D of the four-way valve 12 to be respectively communicated, controlling the first throttling element (14), the second throttling element (22), the third throttling element (17), the first electromagnetic valve (101), the fourth electromagnetic valve (104) and the fifth electromagnetic valve (105) to be opened, and controlling the second electromagnetic valve (102), the third electromagnetic valve (103) and the sixth electromagnetic valve (106) to be closed;
or when the obtained working mode is a double-heat-source non-air-supplementing refrigeration mode, controlling the port A and the port B and the port C and the port D of the four-way valve 12 to be respectively communicated, controlling the first throttling element (14), the second throttling element (22), the third throttling element (17), the fourth electromagnetic valve (104) and the fifth electromagnetic valve (105) to be opened, and controlling the first electromagnetic valve (101), the second electromagnetic valve (102), the third electromagnetic valve (103) and the sixth electromagnetic valve (106) to be closed;
or when the acquired working mode is a single heat source air supplementing and refrigerating mode, controlling the port A and the port B and the port C and the port D of the four-way valve 12 to be respectively communicated, controlling the first throttling element (14), the third throttling element (17), the first electromagnetic valve (101), the second electromagnetic valve (102) and the sixth electromagnetic valve (106) to be opened, and controlling the second throttling element (22), the third electromagnetic valve (103), the fourth electromagnetic valve (104) and the fifth electromagnetic valve (105) to be closed;
or when the acquired working mode is a single-heat-source non-air-supplementing refrigeration mode, controlling the port A and the port B of the four-way valve 12 and the port C and the port D to be respectively communicated, controlling the first throttling element (14), the third throttling element (17) and the sixth electromagnetic valve (106) to be opened, and controlling the second throttling element (22), the first electromagnetic valve (101), the second electromagnetic valve (102), the third electromagnetic valve (103), the fourth electromagnetic valve (104) and the fifth electromagnetic valve (105) to be closed.
8. The control method according to claim 5, wherein,
when the acquired working mode is a defrosting mode, the port A and the port B of the four-way valve 12 are controlled to be communicated, the second throttling element (22) and the fifth solenoid valve (105) are controlled to be opened, and the first throttling element (14), the third throttling element (17), the first solenoid valve (101), the second solenoid valve (102), the third solenoid valve (103), the fourth solenoid valve (104) and the sixth solenoid valve (106) are controlled to be closed.
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| CN112128851B (en) * | 2020-09-14 | 2024-04-12 | 珠海格力电器股份有限公司 | Double-evaporation-temperature heat pump system and control method |
| CN112128852B (en) * | 2020-09-14 | 2024-04-12 | 珠海格力电器股份有限公司 | Double-condensation-temperature heat pump system and control method |
| CN112178845A (en) * | 2020-09-23 | 2021-01-05 | 珠海格力电器股份有限公司 | Double-evaporation-temperature heat pump air conditioning equipment and control method thereof |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102012205200A1 (en) * | 2011-04-04 | 2012-10-04 | Denso Corporation | Refrigerant cycle device |
| CN206037478U (en) * | 2016-07-28 | 2017-03-22 | 宁夏塞上阳光太阳能有限公司 | Air source heat pump system with supplementary evaporation pipeline of solar energy |
| CN107356012A (en) * | 2016-05-09 | 2017-11-17 | 开利公司 | Heat pump and its control method |
| CN107796146A (en) * | 2017-10-20 | 2018-03-13 | 珠海格力电器股份有限公司 | Condenser system, air-conditioning system and control method |
| CN210512235U (en) * | 2019-09-12 | 2020-05-12 | 珠海格力电器股份有限公司 | Heat pump system |
-
2019
- 2019-09-12 CN CN201910865542.8A patent/CN110500804B/en active Active
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102012205200A1 (en) * | 2011-04-04 | 2012-10-04 | Denso Corporation | Refrigerant cycle device |
| CN107356012A (en) * | 2016-05-09 | 2017-11-17 | 开利公司 | Heat pump and its control method |
| CN206037478U (en) * | 2016-07-28 | 2017-03-22 | 宁夏塞上阳光太阳能有限公司 | Air source heat pump system with supplementary evaporation pipeline of solar energy |
| CN107796146A (en) * | 2017-10-20 | 2018-03-13 | 珠海格力电器股份有限公司 | Condenser system, air-conditioning system and control method |
| CN210512235U (en) * | 2019-09-12 | 2020-05-12 | 珠海格力电器股份有限公司 | Heat pump system |
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