CN108375255B - Air conditioner system - Google Patents
Air conditioner system Download PDFInfo
- Publication number
- CN108375255B CN108375255B CN201711471669.9A CN201711471669A CN108375255B CN 108375255 B CN108375255 B CN 108375255B CN 201711471669 A CN201711471669 A CN 201711471669A CN 108375255 B CN108375255 B CN 108375255B
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- Prior art keywords
- heat exchanger
- air conditioner
- pipeline
- conditioner system
- refrigerant
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- 239000003507 refrigerant Substances 0.000 claims abstract description 77
- 238000010438 heat treatment Methods 0.000 claims abstract description 37
- 239000007788 liquid Substances 0.000 claims abstract description 37
- 238000001816 cooling Methods 0.000 claims description 6
- 238000011144 upstream manufacturing Methods 0.000 claims description 4
- 238000004781 supercooling Methods 0.000 abstract description 6
- 230000000694 effects Effects 0.000 abstract description 2
- 238000005057 refrigeration Methods 0.000 description 11
- 238000010586 diagram Methods 0.000 description 6
- 238000001704 evaporation Methods 0.000 description 6
- 230000008020 evaporation Effects 0.000 description 6
- 239000002918 waste heat Substances 0.000 description 4
- 238000000034 method Methods 0.000 description 3
- 238000004378 air conditioning Methods 0.000 description 2
- 238000006467 substitution reaction Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 238000005265 energy consumption Methods 0.000 description 1
- 239000007789 gas Substances 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 238000009834 vaporization Methods 0.000 description 1
- 230000008016 vaporization Effects 0.000 description 1
Classifications
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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
- F25B40/00—Subcoolers, desuperheaters or superheaters
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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
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
- F25B47/022—Defrosting cycles hot gas defrosting
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
- F25B40/02—Subcoolers
-
- 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
- F25B41/30—Expansion means; Dispositions thereof
- F25B41/39—Dispositions with two or more expansion means arranged in series, i.e. multi-stage expansion, on a refrigerant line leading to the same evaporator
-
- 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
- F25B2313/021—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit
- F25B2313/0211—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit the auxiliary heat exchanger being only used during defrosting
-
- 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
- F25B2313/021—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit
- F25B2313/0213—Indoor unit or outdoor unit with auxiliary heat exchanger not forming part of the indoor or outdoor unit the auxiliary heat exchanger being only used during heating
-
- 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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/13—Economisers
-
- 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
- F25B2500/00—Problems to be solved
- F25B2500/09—Improving heat transfers
-
- 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
- F25B2500/00—Problems to be solved
- F25B2500/31—Low ambient temperatures
Landscapes
- 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 belongs to the technical field of air conditioners, and particularly relates to an air conditioner system. In order to improve the heating circulation effect of the air conditioner, the air conditioner system comprises a compressor, an indoor heat exchanger, a first throttling device and an outdoor heat exchanger which are connected in series in a main loop, wherein the main loop is also provided with the heat exchanger and a first gas-liquid separator; one side of the heat exchanger is connected with a first pipeline between the first throttling device and the indoor heat exchanger, and the other side of the heat exchanger is connected with a second pipeline between the first throttling device and the outdoor heat exchanger; the refrigerant passing through the first pipeline and the refrigerant passing through the second pipeline can exchange heat in the heat exchanger; the first gas-liquid separator is positioned in the second pipeline section between the heat exchanger and the outdoor heat exchanger, and a bypass pipeline is arranged between the first gas-liquid separator and the compressor. The invention not only effectively increases the supercooling degree of the refrigerant in the first pipeline, but also can reduce the power consumption of the system and increase the circulating quantity of the refrigerant, thereby improving the heating capacity of the whole system.
Description
Technical Field
The invention belongs to the technical field of air conditioners, and particularly relates to an air conditioner system.
Background
The existing air conditioner system usually forms a refrigeration/heating circulation loop by a condenser, a throttling device, an evaporator and a compressor, wherein a high-temperature high-pressure gaseous refrigerant discharged by the compressor is condensed into low-temperature high-pressure liquid in the condenser, is throttled into low-temperature low-pressure liquid by the throttling device, then enters the evaporator to absorb heat and evaporate, and completes a refrigeration/heating circulation.
when the air conditioner operates in heating, high-temperature and high-pressure gaseous refrigerant is subjected to heat exchange through the condenser to form low-temperature and high-pressure liquid refrigerant, and then is throttled and depressurized through the throttling device to form low-temperature and low-pressure gas-liquid two-phase region refrigerant, and the refrigerant enters the evaporator for heat exchange. The larger the evaporation area, the higher the relative evaporation capacity. The supercooling degree of the low-temperature high-pressure liquid refrigerant can be increased if the heat of the low-temperature high-pressure liquid refrigerant is continuously released, so that the refrigerating and heating capacity of the system circulation is increased. During heat exchange of the refrigerant, more than 95% of heat exchange amount is derived from latent vaporization heat of a two-phase region of the refrigerant, the isobaric specific heat capacity of a one-way region (pure liquid and pure gas) is relatively small, and the heat exchange amount accounts for a small proportion of the total system circulation. In addition, the pressure drop of the gaseous refrigerant in the pipeline is large, which is a main source of the pressure loss of the system refrigerant cycle, and the cycle work load can be increased, namely, the energy consumption of the system cycle is increased.
Further, referring to fig. 3, fig. 3 is a schematic diagram of a cycle in heating operation of the conventional air conditioner. As shown in fig. 3, the actual operating temperature point of the air conditioner during heating operation is generally that a refrigerant with a high temperature of 70 ℃ enters an indoor heat exchanger to exchange heat with an indoor environment with the temperature of 20 ℃, the temperature is reduced to 30 ℃, the refrigerant enters a throttling device after flowing through an online pipe, wherein the temperature (about 30 ℃) between a point B and the throttling device is far higher than the outdoor environment temperature by 7 ℃, the waste heat is wasted, and the supercooling degree of the refrigerant circulation of the system can be increased if the waste heat is absorbed and utilized.
The present invention has been made in view of the above circumstances.
Disclosure of Invention
in order to solve the problems in the prior art, namely to improve the heating circulation effect of the air conditioner, the air conditioner system provided by the invention comprises a compressor, an indoor heat exchanger, a first throttling device and an outdoor heat exchanger which are connected in series in a main loop, wherein the main loop is also provided with the heat exchanger and a first gas-liquid separator; one side of the heat exchanger is connected with a first pipeline between the first throttling device and the indoor heat exchanger, and the other side of the heat exchanger is connected with a second pipeline between the first throttling device and the outdoor heat exchanger; the refrigerant passing through the first pipeline and the refrigerant passing through the second pipeline can exchange heat in the heat exchanger; the first gas-liquid separator is located in a second pipe section between the heat exchanger and the outdoor heat exchanger, and a bypass pipe is provided between the first gas-liquid separator and the compressor.
In a preferred embodiment of the air conditioner system, a second throttling device is disposed in the bypass line, and the second throttling device is configured to control a flow rate of the gaseous refrigerant when the air conditioner system is in heating operation.
in a preferred embodiment of the above air conditioner system, the first pipe passes through one side of the heat exchanger and/or the second pipe passes through the other side of the heat exchanger.
In a preferred embodiment of the above air conditioner system, a third throttling device is further provided in the primary circuit, the third throttling device being located in the first pipe section between the heat exchanger and the indoor heat exchanger.
In a preferred embodiment of the air conditioner system, when the air conditioner system is in heating operation, the third throttling device is in a fully open state, and the first throttling device is used for throttling the refrigerant.
In a preferred embodiment of the air conditioner system, when the air conditioner system is in a cooling operation, the first throttling device is in a fully open state, and the third throttling device is used for throttling a refrigerant.
In a preferred embodiment of the air conditioner system, the compressor is provided with a second gas-liquid separator, and the refrigerant flows back to the compressor after passing through the second gas-liquid separator.
In a preferred embodiment of the above air conditioner system, the bypass line is connected upstream of the second gas-liquid separator.
In a preferred embodiment of the above air conditioner system, the air conditioner system further comprises a mode switching device for switching the air conditioner system between a cooling mode and a heating mode.
In a preferred embodiment of the above air conditioner system, the mode switching device is a four-way valve.
In the technical scheme of the invention, the heat exchanger is additionally arranged in the air conditioner system, and the two sides of the heat exchanger are respectively connected with the first pipeline and the second pipeline, so that the refrigerant in the first pipeline and the refrigerant in the second pipeline can exchange heat at the heat exchanger, thereby not only effectively increasing the supercooling degree of the refrigerant in the first pipeline, but also promoting the evaporation of the refrigerant in the second pipeline, and further improving the heating capacity of the system. In addition, a bypass pipeline is arranged between the first gas-liquid separator and the compressor, and the gaseous refrigerant passing through the first gas-liquid separator can enter the air suction port of the compressor through the bypass pipeline, so that the pressure loss of the part of the gaseous refrigerant in the heating cycle is reduced, namely the pressure of the air suction port of the compressor is increased, the power consumption of the compressor is further reduced, the circulation quantity of the refrigerant in the heating cycle of the air conditioner system is increased, and the purpose of improving the heating quantity is achieved. In addition, the air conditioner of the invention also adopts the mode of arranging the third throttling device, so that when the air conditioner is switched into the refrigeration mode, the third throttling device is used for throttling the refrigerant instead of the first throttling device (at the moment, the first throttling device is in a fully open state), thereby avoiding the phenomenon that the refrigerating capacity is reduced during the refrigeration cycle.
Drawings
FIG. 1 is a schematic block diagram of a first embodiment of an air conditioning system according to the present invention;
FIG. 2 is a schematic diagram of a second embodiment of the air conditioning system of the present invention;
Fig. 3 is a schematic diagram of a cycle in heating operation of a conventional air conditioner.
Detailed Description
In order to make the embodiments, technical solutions and advantages of the present invention more apparent, the technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings, and it is apparent that the embodiments are some, but not all embodiments of the present invention. It should be understood by those skilled in the art that these embodiments are only for explaining the technical principle of the present invention, and are not intended to limit the scope of the present invention.
Referring first to fig. 1, fig. 1 is a schematic structural diagram of a first embodiment of an air conditioner system according to the present invention. As shown in fig. 1, the air conditioner system of the present invention includes a compressor 1, an indoor heat exchanger 2, a first throttle device 3, and an outdoor heat exchanger 4 connected in series in a main circuit, in which a heat exchanger 5 is further provided. For convenience of explanation, a pipeline between the first throttling device 3 and the indoor heat exchanger 2 is taken as a first pipeline M, a pipeline between the first throttling device 3 and the outdoor heat exchanger 4 is taken as a second pipeline N, one side of the heat exchanger 5 is connected with the first pipeline M, and the other side of the heat exchanger 5 is connected with the second pipeline N, as shown in fig. 1: a first line M passes through one side of the heat exchanger 5 and a second line N passes through the other side of the heat exchanger N. The refrigerant passing through the first pipe line M and the refrigerant passing through the second pipe line N can exchange heat in the heat exchanger 5. Furthermore, a first gas-liquid separator 6 is provided in the main circuit, the first gas-liquid separator 6 being located in the section of the second conduit N between the heat exchanger 5 and the outdoor heat exchanger 4, and a bypass conduit L being provided between the first gas-liquid separator 6 and the compressor 1.
In the heating cycle process of the air conditioner, high-temperature and high-pressure gaseous refrigerant discharged by the compressor 1 flows to the indoor heat exchanger 2, heat exchange is carried out in the indoor heat exchanger 2, the refrigerant is changed into low-temperature and high-pressure liquid refrigerant, the refrigerant reaches a point C along the first pipeline M, and the temperature of the refrigerant is about 20 ℃ (the heat in the point is waste heat and is not fully utilized). Then, the refrigerant is throttled by the first throttling device 3 and enters the second pipeline N, and the temperature of the refrigerant at the point D (throttled refrigerant) is about 5 ℃. Because the refrigerant in the first pipeline M and the refrigerant in the second pipeline N have a temperature difference, and both pass through the heat exchanger 5, in this way, the refrigerant in the first pipeline M and the refrigerant in the second pipeline N exchange heat at the heat exchanger 5, not only is the supercooling degree of the refrigerant in the first pipeline M effectively increased (namely, the part of the refrigerant from the point C to the first throttling device 3 continues to release heat and cool), but also the evaporation of the refrigerant in the second pipeline N can be promoted (namely, the low-temperature refrigerant at the point D can evaporate and absorb the residual heat at the point C, which is equivalent to increasing the evaporation area and effectively improving the heat exchange capacity), thereby improving the heating capacity.
next, the refrigerant after heat exchange by the heat exchanger 5 enters the first gas-liquid separator 6, and the gaseous refrigerant separated by the first gas-liquid separator 6 directly flows back to the compressor 1 along the bypass line L, so that the pressure loss of the gaseous refrigerant in the heating cycle is reduced, which is equivalent to increasing the pressure of the suction port of the compressor 1, thereby reducing the power consumption of the compressor 1, increasing the refrigerant circulation amount of the air conditioner system in the heating cycle, and achieving the purpose of increasing the heating capacity. The liquid refrigerant passing through the first gas-liquid separator 6 flows back to the compressor 1 through the outdoor heat exchanger 4. Through the design, the waste heat can be recycled in the heating operation process of the air conditioner, the power consumption of the system can be reduced, and the refrigerant circulation quantity of the air conditioner system during heating circulation is increased, so that the heating quantity of the whole system is improved.
As an example, a second throttling device 7 is disposed on the bypass pipeline L, and when the air conditioner is in heating operation, the second throttling device 7 is used for controlling the flow rate of the gaseous refrigerant, that is, the opening degree of the second throttling device 7 can be adjusted according to the actual operation condition so as to flexibly control the passing amount of the gaseous refrigerant. When the air conditioner is in the refrigeration cycle, the second throttling means 7 may be closed so that the bypass line L does not participate in the refrigeration cycle.
It should be noted that the heat exchanger 5 may be a water tank containing water, or may be in any other suitable form as long as the heat exchange between the refrigerant upstream and downstream of the first throttling device 3 can be performed. In addition, the design can effectively improve the heating capacity for the heating cycle and reduce the cooling capacity for the refrigerating cycle.
As an example, the air conditioner system of the present invention further includes a mode switching device (e.g., a four-way valve Q in fig. 1) for switching the air conditioner system between a cooling mode and a heating mode.
as an example, referring to fig. 2, fig. 2 is a schematic structural diagram of a second embodiment of the air conditioner system of the present invention. As shown in fig. 2, a third throttling device 8 is also provided in the main circuit of the air conditioner system of the present invention, the third throttling device 8 being located in the first pipe line M section between the heat exchanger 5 and the indoor heat exchanger 2. When the air conditioner is in heating operation, the third throttling device 8 is in a fully open state, and the first throttling device 3 is used for throttling the refrigerant. The principle of the air conditioner system in the first embodiment is the same. When the air conditioner system is switched to the refrigerating operation through the four-way valve Q, the first throttling device 3 is in a fully open state, the third throttling device 8 is used for throttling the refrigerant, and meanwhile, the second throttling device 7 is closed. At this time, there is almost no temperature difference between the refrigerants on both sides of the heat exchanger 5, that is, the heat exchanger 5 does not play a role in the process of the refrigeration cycle, and the whole refrigeration cycle is a conventional refrigeration cycle. Thereby avoiding reducing the refrigerating capacity during the refrigerating operation.
Preferably, referring to fig. 1 and 2, the compressor 1 is provided with a second gas-liquid separator 11, and the gaseous refrigerant introduced into the compressor 1 first passes through the second gas-liquid separator 11 and then is sucked into the compressor 1, thereby starting the next cycle. Wherein the bypass line L is connected upstream of the second gas-liquid separator 11.
In summary, the heat exchanger is added in the air conditioner system of the present invention, and two sides of the heat exchanger are respectively connected to the first pipeline and the second pipeline, so that the refrigerant in the first pipeline and the refrigerant in the second pipeline can exchange heat at the heat exchanger, which not only effectively increases the supercooling degree of the refrigerant in the first pipeline, but also promotes the evaporation of the refrigerant in the second pipeline, thereby increasing the heating capacity of the system. In addition, a bypass pipeline is arranged between the first gas-liquid separator and the compressor, and the gaseous refrigerant passing through the first gas-liquid separator can enter the air suction port of the compressor through the bypass pipeline, so that the pressure loss of the part of the gaseous refrigerant in the heating cycle is reduced, namely the pressure of the air suction port of the compressor is increased, the power consumption of the compressor is further reduced, the refrigerant circulation quantity of the air conditioner system in the heating cycle is increased, and the purpose of increasing the heating quantity is achieved. In addition, the air conditioner of the invention also adopts the mode of arranging the third throttling device, so that when the air conditioner is switched into the refrigeration mode, the third throttling device is used for throttling the refrigerant instead of the first throttling device (at the moment, the first throttling device is in a fully open state), thereby avoiding the phenomenon that the refrigerating capacity is reduced during the refrigeration cycle.
So far, the technical solutions of the present invention have 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 the present invention is obviously not limited to these specific embodiments. Equivalent changes or substitutions of related technical features can be made by those skilled in the art without departing from the principle of the invention, and the technical scheme after the changes or substitutions can fall into the protection scope of the invention.
Claims (9)
1. An air conditioner system comprises a compressor, an indoor heat exchanger, a first throttling device and an outdoor heat exchanger which are connected in series in a main loop,
The system is characterized in that a heat exchanger and a first gas-liquid separator are also arranged in the main loop;
One side of the heat exchanger is connected with a first pipeline between the first throttling device and the indoor heat exchanger, and the other side of the heat exchanger is connected with a second pipeline between the first throttling device and the outdoor heat exchanger;
The refrigerant passing through the first pipeline and the refrigerant passing through the second pipeline can exchange heat in the heat exchanger;
The first gas-liquid separator is located in a second pipeline section between the heat exchanger and the outdoor heat exchanger, and a bypass pipeline is arranged between the first gas-liquid separator and the compressor;
A third throttling device is also provided in the primary circuit, the third throttling device being located in the first pipe section between the heat exchanger and the indoor heat exchanger.
2. the air conditioner system as claimed in claim 1, wherein a second throttling device is disposed in the bypass line, and the second throttling device is used for controlling a flow rate of the gaseous refrigerant when the air conditioner system is in heating operation.
3. An air conditioner system as set forth in claim 1 wherein said first conduit passes through one side of said heat exchanger and/or said second conduit passes through the other side of said heat exchanger.
4. The air conditioner system as claimed in claim 1, wherein when the air conditioner system is in heating operation, the third throttling means is in a fully open state, and the first throttling means is used for throttling the refrigerant.
5. The air conditioner system as claimed in claim 1, wherein when the air conditioner system is operated in a cooling mode, the first throttling means is in a fully opened state, and the third throttling means is used for throttling the refrigerant.
6. the air conditioner system as claimed in any one of claims 1 to 5, wherein the compressor is provided with a second gas-liquid separator, and the refrigerant flows back to the compressor after passing through the second gas-liquid separator.
7. The air conditioner system as recited in claim 6, wherein the bypass line is connected upstream of the second gas-liquid separator.
8. The air conditioner system as claimed in any one of claims 1 to 5, further comprising a mode switching device for switching the air conditioner system between a cooling mode and a heating mode.
9. The air conditioner system as claimed in claim 8, wherein said mode switching means is a four-way valve.
Priority Applications (4)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711471669.9A CN108375255B (en) | 2017-12-29 | 2017-12-29 | Air conditioner system |
| EP18894319.5A EP3734199B1 (en) | 2017-12-29 | 2018-11-15 | Air-conditioner system |
| PCT/CN2018/115748 WO2019128517A1 (en) | 2017-12-29 | 2018-11-15 | Air-conditioner system |
| JP2020535567A JP6982692B2 (en) | 2017-12-29 | 2018-11-15 | Air conditioner system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711471669.9A CN108375255B (en) | 2017-12-29 | 2017-12-29 | Air conditioner system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN108375255A CN108375255A (en) | 2018-08-07 |
| CN108375255B true CN108375255B (en) | 2019-12-06 |
Family
ID=63015488
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201711471669.9A Active CN108375255B (en) | 2017-12-29 | 2017-12-29 | Air conditioner system |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP3734199B1 (en) |
| JP (1) | JP6982692B2 (en) |
| CN (1) | CN108375255B (en) |
| WO (1) | WO2019128517A1 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN108375255B (en) * | 2017-12-29 | 2019-12-06 | 青岛海尔空调器有限总公司 | Air conditioner system |
| CN111059615A (en) * | 2019-12-20 | 2020-04-24 | 青岛海尔空调电子有限公司 | Multi-line air conditioning system |
Citations (5)
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|---|---|---|---|---|
| JP2011052884A (en) * | 2009-09-01 | 2011-03-17 | Mitsubishi Electric Corp | Refrigerating air conditioner |
| CN102620458A (en) * | 2011-01-27 | 2012-08-01 | 松下电器产业株式会社 | Refrigeration cycle apparatus |
| CN203432134U (en) * | 2013-07-05 | 2014-02-12 | 广东长菱空调冷气机制造有限公司 | Heat pump system of air source heat pump water heater |
| CN106016535A (en) * | 2016-05-31 | 2016-10-12 | 广东美的制冷设备有限公司 | Enhanced vapor injection air conditioning system and defrosting control method thereof |
| CN107084562A (en) * | 2017-04-13 | 2017-08-22 | 青岛海尔空调器有限总公司 | A kind of control method of air conditioner and air conditioner |
Family Cites Families (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
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Also Published As
| Publication number | Publication date |
|---|---|
| EP3734199A4 (en) | 2021-02-24 |
| EP3734199B1 (en) | 2022-07-27 |
| JP6982692B2 (en) | 2021-12-17 |
| CN108375255A (en) | 2018-08-07 |
| WO2019128517A1 (en) | 2019-07-04 |
| EP3734199A1 (en) | 2020-11-04 |
| JP2021508025A (en) | 2021-02-25 |
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