CN115183404B - Control method of air conditioning system - Google Patents
Control method of air conditioning system Download PDFInfo
- Publication number
- CN115183404B CN115183404B CN202210813942.6A CN202210813942A CN115183404B CN 115183404 B CN115183404 B CN 115183404B CN 202210813942 A CN202210813942 A CN 202210813942A CN 115183404 B CN115183404 B CN 115183404B
- Authority
- CN
- China
- Prior art keywords
- control valve
- heat exchanger
- gas
- outdoor heat
- branch
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 238000004378 air conditioning Methods 0.000 title claims abstract description 69
- 238000000034 method Methods 0.000 title claims abstract description 30
- 239000003507 refrigerant Substances 0.000 claims abstract description 114
- 239000007788 liquid Substances 0.000 claims abstract description 98
- 238000010438 heat treatment Methods 0.000 claims abstract description 21
- 238000001816 cooling Methods 0.000 claims description 11
- 239000012071 phase Substances 0.000 description 37
- 238000010586 diagram Methods 0.000 description 16
- 238000001704 evaporation Methods 0.000 description 9
- 239000007791 liquid phase Substances 0.000 description 7
- 230000008020 evaporation Effects 0.000 description 5
- 230000005494 condensation Effects 0.000 description 4
- 238000009833 condensation Methods 0.000 description 4
- 238000005057 refrigeration Methods 0.000 description 4
- 238000000926 separation method Methods 0.000 description 4
- 230000007613 environmental effect Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000006467 substitution reaction Methods 0.000 description 2
- 238000004781 supercooling Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 1
- 239000002699 waste material Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
- F24F11/41—Defrosting; Preventing freezing
- F24F11/42—Defrosting; Preventing freezing of outdoor units
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/70—Control systems characterised by their outputs; Constructional details thereof
- F24F11/80—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air
- F24F11/83—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers
- F24F11/84—Control systems characterised by their outputs; Constructional details thereof for controlling the temperature of the supplied air by controlling the supply of heat-exchange fluids to heat-exchangers using valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F24—HEATING; RANGES; VENTILATING
- F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
- F24F11/00—Control or safety arrangements
- F24F11/89—Arrangement or mounting of control or safety devices
-
- 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
- F25B41/20—Disposition of valves, e.g. of on-off valves or flow control valves
- F25B41/24—Arrangement of shut-off valves for disconnecting a part of the refrigerant cycle, e.g. an outdoor part
-
- 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
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention relates to the technical field of air conditioners, in particular to an air conditioning system and a control method thereof, and aims to solve the problems that the existing air conditioning system generates larger pressure drop when the flow of a refrigerant is larger and an outdoor heat exchanger is easy to damage in a heating mode. For this purpose, the air conditioning system of the present invention comprises a first outdoor heat exchanger, a gas-liquid separator, a second outdoor heat exchanger, a throttle valve, an indoor heat exchanger and a compressor connected in sequence in a main circuit, characterized in that the air conditioning system further comprises: the control valve assembly is arranged on the first branch and is connected with the gas outlet of the gas-liquid separator and one end of the first outdoor heat exchanger, which is far away from the gas-liquid separator, and is used for controlling the flow of the refrigerant flowing through the first branch; and the first control valve is arranged on the second branch circuit, the second branch circuit bypasses the second outdoor heat exchanger, and the first control valve is used for controlling the flow of the refrigerant flowing through the second branch circuit. The heat exchange performance of the outdoor heat exchanger is guaranteed, and the outdoor heat exchanger is not damaged.
Description
Technical Field
The invention relates to the technical field of air conditioners, and particularly provides an air conditioning system and a control method thereof.
Background
With the improvement of people's level, air conditioner has become an indispensable home appliance. When the air conditioner heats in a low-temperature environment, the evaporation temperature of the outdoor unit is too low when the outdoor unit works as an evaporator, so that frosting of a heat exchanger is easily caused, and the normal operation of the whole air conditioning system is influenced. On the other hand, due to the arrangement or structure of fans and other problems, many heat exchangers have the problem of uneven wind fields; the outdoor heat exchanger with uneven wind fields is more prone to frosting.
In order to improve the heat exchange performance of the heat exchanger, chinese patent (CN 113970126 a) discloses an air conditioner, a control method of the air conditioner, and a storage medium, which divide an outdoor heat exchanger into two, and a gas-liquid separator is additionally provided between the two heat exchangers. In the heating mode, the refrigerant flows through the second heat exchanger, and the redundant gaseous refrigerant is directly bypassed to the air suction port of the compressor through the gas-liquid separator, so that the waste of the area of the heat exchanger is reduced, and the aim of improving the heat exchange effect is fulfilled.
However, the heat exchanger design is suitable for a system with smaller system refrigerant flow, and when the system refrigerant flow is larger, the heat exchanger through which all refrigerants flow first in the heating mode generates larger pressure drop, so that the temperature of the refrigerant is high, and the heat exchanger can be completely scrapped.
Accordingly, there is a need for an air conditioning system and a control method thereof to solve the above-mentioned problems.
Disclosure of Invention
The invention aims to solve the technical problems that the prior air conditioning system generates larger pressure drop when the refrigerant flow is larger in a heating mode, and the outdoor heat exchanger is easy to damage.
In a first aspect, the present invention provides an air conditioning system comprising a first outdoor heat exchanger, a gas-liquid separator, a second outdoor heat exchanger, a throttle valve, an indoor heat exchanger and a compressor connected in sequence in a main circuit, characterized in that the air conditioning system further comprises:
The control valve assembly is arranged on the first branch and is communicated with the gas outlet of the gas-liquid separator and one end, far away from the gas-liquid separator, of the first outdoor heat exchanger, and the control valve assembly is used for controlling the flow rate of the refrigerant flowing through the first branch;
And the first control valve is arranged on the second branch circuit, the second branch circuit bypasses the second outdoor heat exchanger, and the first control valve is used for controlling the flow rate of the refrigerant flowing through the second branch circuit.
In a specific embodiment of the air conditioning system, the control valve assembly includes a check valve and a second control valve connected in series in the first branch, the check valve being configured to allow only refrigerant to flow from the gas outlet of the gas-liquid separator to the end of the first outdoor heat exchanger remote from the gas-liquid separator, and the second control valve being configured to control the flow rate of the refrigerant flowing through the first branch.
In a specific embodiment of the air conditioning system, the control valve assembly includes only a second control valve, and the second control valve is used for controlling the flow rate of the refrigerant flowing through the first branch.
In a specific embodiment of the foregoing air conditioning system, the air conditioning system further includes a third control valve disposed on a third branch, where the third branch is connected to one end of the first outdoor heat exchanger near the gas-liquid separator and one end of the second outdoor heat exchanger near the gas-liquid separator, and the third control valve is configured to control a flow rate of the refrigerant flowing through the third branch.
In a specific embodiment of the air conditioning system, the first control valve, the second control valve and the third control valve are all electric ball valves.
In a second aspect, the present invention provides a control method for an air conditioning system as described above, the control method comprising the steps of:
in a heating mode, the first control valve and the second control valve are opened.
In a specific embodiment of the above control method of an air conditioning system, the control method further includes:
And in a heating mode, the opening degrees of the first control valve and the second control valve are adjusted according to the current operation working condition of the air conditioning system.
In a specific embodiment of the control method of an air conditioning system, the air conditioning system further includes a third control valve disposed on a third branch, the third branch being connected to one end of the first outdoor heat exchanger near the gas-liquid separator and one end of the second outdoor heat exchanger near the gas-liquid separator, the third control valve being configured to control a flow rate of the refrigerant flowing through the third branch,
The control method further includes:
And in the heating mode, closing the third control valve.
In a third aspect, the present invention provides a control method for an air conditioning system as described above, the control method comprising the steps of:
In the cooling mode, the first control valve and the second control valve are closed.
In a specific embodiment of the control method of an air conditioning system, the air conditioning system further includes a third control valve disposed on a third branch, the third branch being connected to one end of the first outdoor heat exchanger near the gas-liquid separator and one end of the second outdoor heat exchanger near the gas-liquid separator, the third control valve being configured to control a flow rate of the refrigerant flowing through the third branch,
The control method further includes:
In the cooling mode, the third control valve is opened.
Under the condition that the technical scheme is adopted, when the air conditioning system is in a heating mode, part of refrigerant flows in from the second outdoor heat exchanger, flows into the gas-liquid separator after heat exchange by the second heat exchanger, the other part of refrigerant flows into the gas-liquid separator through the first control valve, the gas-phase refrigerant separated by the gas-liquid separator flows out through the control valve assembly, and the liquid-phase refrigerant separated by the gas-liquid separator flows out after heat exchange by the first outdoor heat exchanger.
The first control valve divides the throttled refrigerant, so that the amount of the refrigerant entering the second outdoor heat exchanger is reduced, the excessive flow of the refrigerant entering the second outdoor heat exchanger can be avoided, the pressure drop of the second outdoor heat exchanger is greatly reduced, the heat exchange performance of the second outdoor heat exchanger is ensured, and the second outdoor heat exchanger cannot be damaged. The gas-liquid separator separates the gas-phase refrigerant and the gas-phase refrigerant flows out through the control valve assembly, so that the excessive refrigerant quantity of the first outdoor heat exchanger can be avoided, and meanwhile, the pressure drop of the first outdoor heat exchanger is greatly reduced. The heat exchange performance of the first outdoor heat exchanger is guaranteed, and the first outdoor heat exchanger is not damaged. In summary, the air conditioning system not only ensures the heat exchange performance of the outdoor heat exchanger, but also does not damage the outdoor heat exchanger.
Drawings
Preferred embodiments of the present invention are described below with reference to the accompanying drawings, in which:
fig. 1 is a schematic structural diagram of an air conditioning system according to a first embodiment of the present invention;
Fig. 2 is a schematic diagram of a second structure of an air conditioning system according to a first embodiment of the present invention;
fig. 3 is a schematic diagram of an air conditioning system according to a first embodiment of the present invention;
Fig. 4 is a schematic structural diagram of an air conditioning system according to a first embodiment of the present invention;
fig. 5 is a schematic structural diagram of an air conditioning system according to a second embodiment of the present invention;
fig. 6 is a schematic structural diagram of an air conditioning system according to a second embodiment of the present invention;
fig. 7 is a schematic diagram III of an air conditioning system according to a second embodiment of the present invention;
Fig. 8 is a schematic diagram of an air conditioning system according to a second embodiment of the present invention.
List of reference numerals:
1. A first outdoor heat exchanger; 2. a gas-liquid separator; 3. a second outdoor heat exchanger; 4. a control valve assembly; 41. a one-way valve; 42. a second control valve; 5. a first control valve; 6. a compressor; 7. an indoor heat exchanger; 8. a throttle valve; 9. and a third control valve.
Detailed Description
Preferred embodiments of the present invention are described below with reference to the accompanying drawings. It should be understood by those skilled in the art that these embodiments are merely for explaining the technical principles of the present invention, and are not intended to limit the scope of the present invention.
It should be noted that in the description of the present invention, 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.
Furthermore, it should be noted that, in the description of the present invention, unless explicitly stated and limited otherwise, the terms "disposed" and "connected" should be interpreted broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be directly connected, can be indirectly connected through an intermediate medium, and can also be communicated with the inside of two elements. The specific meaning of the above terms in the present invention can be understood by those skilled in the art according to the specific circumstances.
The outdoor heat exchanger aims at solving the problems that the existing air conditioning system generates larger pressure drop when the refrigerant flow is larger in a heating mode and the outdoor heat exchanger is easy to damage.
Fig. 1 is a schematic structural diagram of an air conditioning system according to a first embodiment of the present invention, wherein a direction indicated by an arrow is a flow direction of a refrigerant in a heating mode; fig. 2 is a schematic structural diagram of a second embodiment of an air conditioning system according to the present invention, in which the direction indicated by the arrow is the flow direction of the refrigerant in the cooling mode.
As shown in fig. 1 and 2, the present embodiment discloses an air conditioning system including a first outdoor heat exchanger 1, a gas-liquid separator 2, a second outdoor heat exchanger 3, a throttle valve 8, an indoor heat exchanger 7, and a compressor 6, which are sequentially connected in a main circuit.
The air conditioning system further comprises a control valve assembly 4 and a first control valve 5, wherein the control valve assembly 4 is arranged on the first branch, and the first branch is connected with the gas outlet of the gas-liquid separator 2 and one end of the first outdoor heat exchanger 1, which is far away from the gas-liquid separator 2, namely, the first branch is connected with the gas outlet of the gas-liquid separator 2 and one end of the first outdoor heat exchanger 1, which is connected with the compressor 6. Specifically, the control valve assembly 4 includes a check valve 41 and a second control valve 42, the check valve 41 and the second control valve 42 being connected in series on the first branch, the check valve 41 being arranged to allow only the refrigerant to flow directly from the gas outlet of the gas-liquid separator 2 to the suction port of the compressor 6. The second control valve 42 is used for controlling the flow rate of the refrigerant flowing through the first branch, and the second control valve 42 is arranged near the gas-liquid separator 2. The second control valve 42 is embodied as an electrically-operated ball valve, and in other embodiments, the second control valve 42 may be selected as a solenoid valve, etc. as desired by those skilled in the art.
The first control valve 5 is disposed on the second branch, specifically, the second branch bypasses the second outdoor heat exchanger 3, that is, two ends of the second branch are respectively communicated with two ends of the second outdoor heat exchanger 3. The first electromagnetic valve is used for controlling the flow of the refrigerant flowing through the second branch. The first control valve 5 is in particular an electrically operated ball valve, and in other embodiments, the first control valve 5 may be selected as a solenoid valve or the like as desired by a person skilled in the art.
The control method of the air conditioning system comprises the following steps: in the heating mode, the first control valve 5 and the second control valve 42 are opened; and/or in the cooling mode, the first control valve 5 and the second control valve 42 are closed.
As shown in fig. 1, in the heating mode, the first control valve 5 and the second control valve 42 are both opened, and the high-temperature high-pressure gas-phase refrigerant from the compressor 6 is condensed and released through the indoor heat exchanger 7 and throttled into a low-temperature low-pressure gas-liquid two-phase state through the throttle valve 8. Part of the refrigerant coming out of the throttle valve 8 enters the second outdoor heat exchanger 3, evaporates at the second outdoor heat exchanger 3 and enters the gas-liquid separator 2 in a gas-liquid two-phase state; the other part enters the second branch and enters the gas-liquid separator 2 through the first control valve 5. The gas-liquid separator 2 separates the two-phase refrigerant into gas and liquid, the gas-phase refrigerant enters the first branch through the gas outlet of the gas-liquid separator 2, directly flows to the air suction port of the compressor 6 through the second control valve 42 and the one-way valve, and the liquid-phase refrigerant flows to the first outdoor heat exchanger 1 to be continuously evaporated into superheated gas and then flows to the air suction port of the compressor 6.
The throttled gas-liquid two-phase refrigerant firstly flows through the second outdoor heat exchanger 3 to be evaporated, then flows through the gas-liquid separator 2 to be separated, and the evaporated gas-phase refrigerant is directly communicated to the air suction port of the compressor 6 through the first branch and does not continue to exchange heat in the first heat exchanger, so that the heat exchange area of the first heat exchanger is saved, and the overall heat exchange efficiency of the outdoor heat exchanger is improved. The evaporating temperature can be obviously improved, and the frosting performance is obviously improved.
Furthermore, the opening degree of the second control valve 42 is adjusted to regulate the gas-liquid separation rate, so as to avoid the situation that the gas-liquid separation speed is too high, the gas-phase refrigerant is excessively lost, and the low pressure is too low.
The first control valve 5 may bypass the second outdoor heat exchanger 3, and the specific opening degree is determined according to the refrigerant flow rate. The opening degree of the first control valve 5 is larger as the refrigerant flow rate of the air conditioning system is larger. The first control valve 5 divides the throttled refrigerant, so that the amount of the refrigerant entering the second outdoor heat exchanger 3 is reduced, the excessive flow of the refrigerant entering the second outdoor heat exchanger 3 can be avoided, the pressure drop of the second outdoor heat exchanger 3 is greatly reduced, the heat exchange performance of the outdoor heat exchanger is ensured, and the second outdoor heat exchanger 3 is not damaged. The opening degree of the first control valve 5 and the opening degree of the second control valve 42 are adjusted to regulate the refrigerant flow of different flow paths, so that the evaporation temperature of the heat exchanger can be controlled, and the heat exchange performance of the outdoor heat exchanger can be further improved. As the heat exchanger has the adjusting capability of changing the evaporating temperature, the working temperature range of each environmental working condition of the heat exchanger is greatly expanded, the anti-frosting capability is improved, and the heat exchanging capability is comprehensively improved.
As shown in fig. 2, in the refrigeration mode, the first control valve 5 and the second control valve 42 are closed, the high-temperature high-pressure gas-phase refrigerant from the compressor 6 is condensed and converted into a gas-liquid two-phase refrigerant through the first outdoor heat exchanger 1, and then enters the gas-liquid separator 2, and the gas-liquid two-phase refrigerant continues to enter the second outdoor heat exchanger 3 for condensation and heat exchange. The supercooled liquid-phase refrigerant passes through the throttle valve 8, flows into the indoor heat exchanger 7 for evaporation and refrigeration, and finally flows back to the compressor 6. Although the pressure drop of the outdoor heat exchanger is slightly larger due to the fact that the refrigerant bypass is not split, the pressure drop has little influence on performance because the refrigerant in the outdoor heat exchanger is in a condensation heat exchange state. Furthermore, the supercooling degree before the throttle valve 8 can be ensured without bypass diversion.
Fig. 3 is a schematic structural diagram III of an air conditioning system according to a first embodiment of the present invention, in which a direction indicated by an arrow is a flow direction of a refrigerant in a heating mode; fig. 4 is a schematic structural diagram of an air conditioning system according to a first embodiment of the present invention, where the direction indicated by the arrow is the flow direction of the refrigerant in the cooling mode.
As shown in fig. 3 and 4, the air conditioning system in the present embodiment preferably further includes a third control valve 9 disposed on a third branch line, the third branch line communicating one end of the first outdoor heat exchanger 1 near the gas-liquid separator 2 and one end of the second outdoor heat exchanger 3 near the gas-liquid separator 2, the third control valve 9 being for controlling the flow rate of the refrigerant flowing through the third branch line. The third control valve 9 is in particular an electrically operated ball valve, and in other embodiments the first control valve 5 may be selected as a solenoid valve or the like as desired by a person skilled in the art.
The control method of the air conditioning system comprises the following steps: as shown in fig. 3, in the heating mode, both the first control valve 5 and the second control valve 42 are opened, and the third control valve 9 is closed. The high-temperature high-pressure gas-phase refrigerant from the compressor 6 is condensed and released by the indoor heat exchanger 7, and is throttled into a low-temperature low-pressure gas-liquid two-phase state by the throttle valve 8. Part of the refrigerant coming out of the throttle valve 8 enters the second outdoor heat exchanger 3, evaporates at the second outdoor heat exchanger 3, and enters the gas-liquid separator 2 in a gas-liquid two-phase state. The other part of the refrigerant enters the gas-liquid separator 2 through the second branch through the first control valve 5, the gas-liquid separator 2 separates the two-phase refrigerant into gas and liquid, the gas-phase refrigerant enters the first branch through the gas outlet of the gas-liquid separator 2, directly flows to the air suction port of the compressor 6 through the second control valve 42 and the one-way valve, and the liquid-phase refrigerant flows to the first outdoor heat exchanger 1 to be continuously evaporated into superheated gas and then flows to the air suction port of the compressor 6.
As shown in fig. 4, in the cooling mode, the first control valve 5 and the second control valve 42 are closed, the third control valve 9 is opened, and the opening degree of the third control valve 9 is maximized. The gas-liquid two-phase refrigerant flowing out of the first outdoor heat exchanger 1 enters a third branch and flows to the second outdoor heat exchanger 3 through a third control valve 9. Since the refrigerant flows through the gas-liquid separator 2 to have a pressure drop, but hardly has a pressure drop through the third branch, the refrigerant flowing out of the first outdoor heat exchanger 1 flows through the third branch to the second outdoor heat exchanger 3. The refrigerant does not flow through the gas-liquid separator 2 to reduce the pressure drop of the refrigerant, and furthermore, the refrigerant does not flow through the gas-liquid separator 2 any more to reduce the loss of the gas-liquid separator 2.
Example two
Fig. 5 is a schematic structural diagram of an air conditioning system according to a second embodiment of the present invention, in which a direction indicated by an arrow is a flow direction of a refrigerant in a heating mode; fig. 6 is a schematic structural diagram of a second embodiment of an air conditioning system according to the present invention, in which the direction indicated by the arrow is the flow direction of the refrigerant in the cooling mode.
As shown in fig. 5 and 6, an air conditioning system is disclosed in the present embodiment, and the structure of the air conditioning system in the present embodiment is substantially the same as that of the air conditioning system in the first embodiment, except for the structure of the control valve assembly 4.
The control valve assembly 4 comprises only the second control valve 42, the second control valve 42 being arranged on the first branch, the first branch being connected to the gas outlet of the gas-liquid separator 2 and to the end of the first outdoor heat exchanger 1 remote from the gas-liquid separator 2, i.e. the first branch being connected to the gas outlet of the gas-liquid separator 2 and to the end of the first outdoor heat exchanger 1 near the compressor.
The control method of the air conditioning system comprises the following steps: as shown in fig. 5, in the heating mode, the first control valve 5 and the second control valve 42 are both opened, and the high-temperature high-pressure gas-phase refrigerant from the compressor 6 is condensed and released through the indoor heat exchanger 7, and throttled into a low-temperature low-pressure gas-liquid two-phase state through the throttle valve 8. Part of the refrigerant coming out of the throttle valve 8 enters the second outdoor heat exchanger 3, evaporates at the second outdoor heat exchanger 3 and enters the gas-liquid separator 2 in a gas-liquid two-phase state; the other part enters the second branch and enters the gas-liquid separator 2 through the first control valve 5. The gas-liquid separator 2 separates the two-phase refrigerant into gas and liquid, the gas-phase refrigerant enters the first branch through the gas outlet of the gas-liquid separator 2, flows to the air suction port of the compressor 6 through the second control valve 42, and the liquid-phase refrigerant flows to the first outdoor heat exchanger 1 to be continuously evaporated into superheated gas and then flows to the air suction port of the compressor 6.
The throttled gas-liquid two-phase refrigerant firstly flows through the second outdoor heat exchanger 3 to be evaporated, then flows through the gas-liquid separator 2 to be separated, and the evaporated gas-phase refrigerant is directly communicated to the air suction port of the compressor 6 through the first branch and does not continue to exchange heat in the first heat exchanger, so that the heat exchange area of the first heat exchanger is saved, and the overall heat exchange efficiency of the outdoor heat exchanger is improved. The evaporating temperature can be obviously improved, and the frosting performance is obviously improved.
Furthermore, the opening degree of the second control valve 42 is adjusted to regulate the gas-liquid separation rate, so as to avoid the situation that the gas-liquid separation speed is too high, the gas-phase refrigerant is excessively lost, and the low pressure is too low.
The first control valve 5 may bypass the second outdoor heat exchanger 3, and the specific opening degree is determined according to the refrigerant flow rate. The opening degree of the first control valve 5 is larger as the refrigerant flow rate of the air conditioning system is larger. The first control valve 5 divides the throttled refrigerant, so that the amount of the refrigerant entering the second outdoor heat exchanger 3 is reduced, the excessive flow of the refrigerant entering the second outdoor heat exchanger 3 can be avoided, the pressure drop of the second outdoor heat exchanger 3 is greatly reduced, the heat exchange performance of the outdoor heat exchanger is ensured, and the second outdoor heat exchanger 3 is not damaged. The opening degree of the first control valve 5 and the opening degree of the second control valve 42 are adjusted to regulate the refrigerant flow of different flow paths, so that the evaporation temperature of the heat exchanger can be controlled, and the heat exchange performance of the outdoor heat exchanger can be further improved. As the heat exchanger has the adjusting capability of changing the evaporating temperature, the working temperature range of each environmental working condition of the heat exchanger is greatly expanded, the anti-frosting capability is improved, and the heat exchanging capability is comprehensively improved.
As shown in fig. 6, in the refrigeration mode, the first control valve 5 and the second control valve 42 are both closed, and the high-temperature and high-pressure gas-phase refrigerant from the compressor 6 is condensed and converted into a gas-liquid two-phase refrigerant through the first outdoor heat exchanger 1, and then enters the gas-liquid separator 2, and the gas-liquid two-phase refrigerant continues to enter the second outdoor heat exchanger 3 for condensation and heat exchange. The supercooled liquid-phase refrigerant passes through the throttle valve 8, flows into the indoor heat exchanger 7 for evaporation and refrigeration, and finally flows back to the compressor 6. Although the pressure drop of the outdoor heat exchanger is slightly larger due to the fact that the refrigerant bypass is not split, the pressure drop has little influence on performance because the refrigerant in the outdoor heat exchanger is in a condensation heat exchange state. Furthermore, the supercooling degree before the throttle valve 8 can be ensured without bypass diversion.
Fig. 7 is a schematic structural diagram III of an air conditioning system according to a second embodiment of the present invention, in which a direction indicated by an arrow is a flow direction of a refrigerant in a heating mode; fig. 8 is a schematic structural diagram of an air conditioning system according to a second embodiment of the present invention, where the direction indicated by the arrow is the flow direction of the refrigerant in the cooling mode.
As shown in fig. 7 and 8, the air conditioning system in the present embodiment preferably further includes a third control valve 9 provided on a third branch line, the third branch line communicating one end of the first outdoor heat exchanger 1 near the gas-liquid separator 2 and one end of the second outdoor heat exchanger 3 near the gas-liquid separator 2, the third control valve 9 being for controlling the flow rate of the refrigerant flowing through the third branch line.
The control method of the air conditioning system comprises the following steps: as shown in fig. 7, in the heating mode, both the first control valve 5 and the second control valve 42 are opened, and the third control valve 9 is closed. The high-temperature high-pressure gas-phase refrigerant from the compressor 6 is condensed and released by the indoor heat exchanger 7, and is throttled into a low-temperature low-pressure gas-liquid two-phase state by the throttle valve 8. Part of the refrigerant coming out of the throttle valve 8 enters the second outdoor heat exchanger 3, evaporates at the second outdoor heat exchanger 3, and enters the gas-liquid separator 2 in a gas-liquid two-phase state. The other part of the refrigerant enters the gas-liquid separator 2 through the second branch through the first control valve 5, the gas-liquid separator 2 separates the two-phase refrigerant into gas and liquid, the gas-phase refrigerant enters the first branch through the gas outlet of the gas-liquid separator 2, directly flows to the air suction port of the compressor 6 through the second control valve 42, and the liquid-phase refrigerant flows to the first outdoor heat exchanger 1 to be continuously evaporated into superheated gas and then flows to the air suction port of the compressor 6.
As shown in fig. 8, in the cooling mode, both the first control valve 5 and the second control valve 42 are closed, the third control valve 9 is opened, and the opening degree of the third control valve 9 is opened to the maximum.
The gas-liquid two-phase refrigerant flowing out of the first outdoor heat exchanger 1 enters a third branch and flows to the second outdoor heat exchanger 3 through a third control valve 9. Since the refrigerant flows through the gas-liquid separator 2 to have a pressure drop, but hardly has a pressure drop through the third branch, the refrigerant flowing out of the first outdoor heat exchanger 1 flows through the third branch to the second outdoor heat exchanger 3. The refrigerant does not flow through the gas-liquid separator 2 to reduce the pressure drop of the refrigerant, and furthermore, the refrigerant does not flow through the gas-liquid separator 2 any more to reduce the loss of the gas-liquid separator 2.
Thus far, the technical solution of the present invention has been described in connection with the preferred embodiments shown in the drawings, but it is easily understood by those skilled in the art that the scope of protection of the present invention is not limited to these specific embodiments. Equivalent modifications and substitutions for related technical features may be made by those skilled in the art without departing from the principles of the present invention, and such modifications and substitutions will fall within the scope of the present invention.
Claims (6)
1. A control method of an air conditioning system, characterized in that the air conditioning system comprises a first outdoor heat exchanger (1), a gas-liquid separator (2), a second outdoor heat exchanger (3), a throttle valve (8), an indoor heat exchanger (7) and a compressor (6) which are sequentially connected in a main circuit, the air conditioning system further comprising:
A control valve assembly (4) arranged on a first branch, wherein the first branch is communicated with a gas outlet of the gas-liquid separator (2) and one end of the first outdoor heat exchanger (1) far away from the gas-liquid separator (2), and the control valve assembly (4) is used for controlling the flow rate of a refrigerant flowing through the first branch;
A first control valve (5) provided on a second branch path bypassing the second outdoor heat exchanger (3), the first control valve (5) being configured to control a flow rate of the refrigerant flowing through the second branch path;
The control valve assembly (4) comprises a one-way valve (41) and a second control valve (42) connected in series in the first branch, the one-way valve (41) being arranged to allow refrigerant to flow only from the gas outlet of the gas-liquid separator (2) to the end of the first outdoor heat exchanger (1) remote from the gas-liquid separator (2), the second control valve (42) being arranged to control the flow of refrigerant through the first branch; or (b)
-The control valve assembly (4) comprises only a second control valve (42), the second control valve (42) being adapted to control the flow of refrigerant through the first branch;
the control method comprises the following steps:
-opening the first control valve (5) and the second control valve (42) in heating mode;
In the cooling mode, the first control valve (5) and the second control valve (42) are closed.
2. The control method of an air conditioning system according to claim 1, characterized in that the air conditioning system further comprises a third control valve (9) provided on a third branch, the third branch communicating an end of the first outdoor heat exchanger (1) near the gas-liquid separator (2) and an end of the second outdoor heat exchanger (3) near the gas-liquid separator (2), the third control valve (9) being for controlling a flow rate of refrigerant flowing through the third branch.
3. The control method of an air conditioning system according to claim 2, characterized in that the first control valve (5), the second control valve (42) and the third control valve (9) are all electric ball valves.
4. The control method of an air conditioning system according to claim 1, characterized in that the control method further comprises:
And in a heating mode, the opening degrees of the first control valve (5) and the second control valve (42) are adjusted according to the current operation working condition of the air conditioning system.
5. The control method of an air conditioning system according to claim 1 or 4, characterized in that the air conditioning system further comprises a third control valve (9) provided on a third branch, the third branch communicating an end of the first outdoor heat exchanger (1) near the gas-liquid separator (2) and an end of the second outdoor heat exchanger (3) near the gas-liquid separator (2), the third control valve (9) being for controlling a flow rate of refrigerant flowing through the third branch;
The control method further includes:
in heating mode, the third control valve (9) is closed.
6. The control method of an air conditioning system according to claim 1, characterized in that the air conditioning system further comprises a third control valve (9) provided on a third branch, the third branch communicating an end of the first outdoor heat exchanger (1) near the gas-liquid separator (2) and an end of the second outdoor heat exchanger (3) near the gas-liquid separator (2), the third control valve (9) being for controlling a flow rate of refrigerant flowing through the third branch;
The control method further includes:
in the cooling mode, the third control valve (9) is opened.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210813942.6A CN115183404B (en) | 2022-07-11 | 2022-07-11 | Control method of air conditioning system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210813942.6A CN115183404B (en) | 2022-07-11 | 2022-07-11 | Control method of air conditioning system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN115183404A CN115183404A (en) | 2022-10-14 |
| CN115183404B true CN115183404B (en) | 2024-06-07 |
Family
ID=83516442
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210813942.6A Active CN115183404B (en) | 2022-07-11 | 2022-07-11 | Control method of air conditioning system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN115183404B (en) |
Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08159588A (en) * | 1994-12-07 | 1996-06-21 | Toshiba Corp | Multi-room type air conditioner |
| JP2002243284A (en) * | 2001-02-20 | 2002-08-28 | Fujitsu General Ltd | Air conditioner |
| JP2007163080A (en) * | 2005-12-16 | 2007-06-28 | Fujitsu General Ltd | Air conditioner |
| JP2010032109A (en) * | 2008-07-29 | 2010-02-12 | Hitachi Appliances Inc | Air conditioner |
| JP2012063083A (en) * | 2010-09-16 | 2012-03-29 | Daikin Industries Ltd | Heat source unit |
| KR20130103887A (en) * | 2012-03-12 | 2013-09-25 | 한라비스테온공조 주식회사 | Heat pump system for vehicle |
| CN105066255A (en) * | 2015-09-01 | 2015-11-18 | 珠海格力电器股份有限公司 | Air conditioning system with continuous heat supply function in defrosting process |
| CN204943956U (en) * | 2015-07-09 | 2016-01-06 | 广东美的暖通设备有限公司 | A kind of efficient cold and warm type air-conditioning system |
| CN205065908U (en) * | 2015-09-01 | 2016-03-02 | 珠海格力电器股份有限公司 | Air conditioning system that defrosting in -process has lasting heat supply function |
| WO2019077906A1 (en) * | 2017-10-16 | 2019-04-25 | 株式会社デンソー | Heat pump cycle |
| EP3517859A1 (en) * | 2018-01-24 | 2019-07-31 | Panasonic Intellectual Property Management Co., Ltd. | Refrigeration cycle apparatus |
| CN211233143U (en) * | 2019-12-29 | 2020-08-11 | 青岛奥利凯中央空调有限公司 | Intelligent proportional control type multifunctional temperature-regulating dehumidifying unit |
-
2022
- 2022-07-11 CN CN202210813942.6A patent/CN115183404B/en active Active
Patent Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH08159588A (en) * | 1994-12-07 | 1996-06-21 | Toshiba Corp | Multi-room type air conditioner |
| JP2002243284A (en) * | 2001-02-20 | 2002-08-28 | Fujitsu General Ltd | Air conditioner |
| JP2007163080A (en) * | 2005-12-16 | 2007-06-28 | Fujitsu General Ltd | Air conditioner |
| JP2010032109A (en) * | 2008-07-29 | 2010-02-12 | Hitachi Appliances Inc | Air conditioner |
| JP2012063083A (en) * | 2010-09-16 | 2012-03-29 | Daikin Industries Ltd | Heat source unit |
| KR20130103887A (en) * | 2012-03-12 | 2013-09-25 | 한라비스테온공조 주식회사 | Heat pump system for vehicle |
| CN204943956U (en) * | 2015-07-09 | 2016-01-06 | 广东美的暖通设备有限公司 | A kind of efficient cold and warm type air-conditioning system |
| CN105066255A (en) * | 2015-09-01 | 2015-11-18 | 珠海格力电器股份有限公司 | Air conditioning system with continuous heat supply function in defrosting process |
| CN205065908U (en) * | 2015-09-01 | 2016-03-02 | 珠海格力电器股份有限公司 | Air conditioning system that defrosting in -process has lasting heat supply function |
| WO2019077906A1 (en) * | 2017-10-16 | 2019-04-25 | 株式会社デンソー | Heat pump cycle |
| EP3517859A1 (en) * | 2018-01-24 | 2019-07-31 | Panasonic Intellectual Property Management Co., Ltd. | Refrigeration cycle apparatus |
| CN211233143U (en) * | 2019-12-29 | 2020-08-11 | 青岛奥利凯中央空调有限公司 | Intelligent proportional control type multifunctional temperature-regulating dehumidifying unit |
Also Published As
| Publication number | Publication date |
|---|---|
| CN115183404A (en) | 2022-10-14 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP3734167B1 (en) | Air conditioner system | |
| CN107178833B (en) | Heat recovery external machine system and air conditioning system | |
| JP6895901B2 (en) | Air conditioner | |
| EP3483523A1 (en) | Refrigeration cycle apparatus and air-conditioning apparatus provided with same | |
| CN210832604U (en) | Air conditioner | |
| EP2568232A2 (en) | Air conditioner | |
| CN109386985B (en) | Two-pipe jet enthalpy-increasing outdoor unit and multi-split system | |
| US20240102700A1 (en) | Heating, Ventilation, and Air-Conditioning Systems and Methods | |
| CN112032912A (en) | Control method of multi-connected air conditioning system | |
| CN112013515B (en) | Control method of air conditioner | |
| US9874383B2 (en) | Air conditioner | |
| CN104949297B (en) | Air-conditioner set and its compress control method | |
| CN112013471B (en) | Air conditioner and control method thereof | |
| EP3734192B1 (en) | Air conditioner system | |
| CN115183404B (en) | Control method of air conditioning system | |
| CN112013472A (en) | Air conditioner and control method thereof | |
| CN112013474A (en) | Air conditioner and control method thereof | |
| CN112013473A (en) | Control method of air conditioner | |
| CN213089945U (en) | Air conditioner | |
| CN214701327U (en) | Centrifugal cascade high-pressure ratio series unit | |
| KR20190088693A (en) | Method for controlling multi-type air conditioner | |
| CN110207419B (en) | Multi-split system | |
| CN108759150B (en) | Air conditioning system and control method thereof | |
| CN112797660A (en) | Air conditioner and control method thereof | |
| CN112728800A (en) | Air conditioner |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant |