CN106766327A - Air conditioner - Google Patents
Air conditioner Download PDFInfo
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- CN106766327A CN106766327A CN201611072447.5A CN201611072447A CN106766327A CN 106766327 A CN106766327 A CN 106766327A CN 201611072447 A CN201611072447 A CN 201611072447A CN 106766327 A CN106766327 A CN 106766327A
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- cavity
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- heat exchanger
- air conditioner
- air
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- 239000007788 liquid Substances 0.000 claims abstract description 117
- 238000004781 supercooling Methods 0.000 claims abstract description 63
- 238000005507 spraying Methods 0.000 claims abstract description 37
- 238000002347 injection Methods 0.000 claims description 9
- 239000007924 injection Substances 0.000 claims description 9
- 238000001816 cooling Methods 0.000 claims description 7
- 238000004891 communication Methods 0.000 claims description 5
- 238000010438 heat treatment Methods 0.000 abstract description 26
- 230000001502 supplementing effect Effects 0.000 abstract description 5
- 238000007906 compression Methods 0.000 description 100
- 230000006835 compression Effects 0.000 description 91
- 239000003507 refrigerant Substances 0.000 description 39
- 239000007921 spray Substances 0.000 description 14
- 230000000694 effects Effects 0.000 description 8
- 238000000034 method Methods 0.000 description 5
- 238000010586 diagram Methods 0.000 description 4
- 238000006073 displacement reaction Methods 0.000 description 3
- 238000001704 evaporation Methods 0.000 description 3
- 230000008020 evaporation Effects 0.000 description 3
- 238000004804 winding Methods 0.000 description 3
- 238000010521 absorption reaction Methods 0.000 description 2
- 230000008030 elimination Effects 0.000 description 2
- 238000003379 elimination reaction Methods 0.000 description 2
- 238000005516 engineering process Methods 0.000 description 2
- 238000002309 gasification Methods 0.000 description 2
- 230000030279 gene silencing Effects 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000005057 refrigeration Methods 0.000 description 2
- 230000001932 seasonal effect Effects 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 230000002457 bidirectional effect Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000009833 condensation Methods 0.000 description 1
- 230000005494 condensation Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 208000002925 dental caries Diseases 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 239000003921 oil Substances 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 239000013526 supercooled liquid Substances 0.000 description 1
- 239000013589 supplement Substances 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
- 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
- F25B31/006—Cooling of compressor or motor
- F25B31/008—Cooling of compressor or motor by injecting a liquid
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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
- F25B40/02—Subcoolers
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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
- F25B41/40—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
- F25B2500/00—Problems to be solved
- F25B2500/08—Exceeding a certain temperature value in a refrigeration component or cycle
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Other Air-Conditioning Systems (AREA)
Abstract
The invention provides an air conditioner which comprises a compressor, a first heat exchanger, an air supplementing and supercooling device, a second heat exchanger, a gas-liquid separator and a liquid spraying pipeline, wherein the compressor, the first heat exchanger, the air supplementing and supercooling device, the second heat exchanger, the gas-liquid separator and the liquid spraying pipeline are communicated. The pump body structure of the compressor comprises at least one cylinder, the cylinder comprises a main working cavity and an auxiliary working cavity, and an air suction port of the auxiliary working cavity is selectively communicated with a gas-liquid separator or an air supply supercooling device. The first end of the liquid spraying pipeline is communicated with the first heat exchanger, and the second end of the liquid spraying pipeline is communicated with the main working cavity. The air suction ports of the auxiliary working cavity are selectively communicated with the gas-liquid separator or the air supply supercooling device, and meanwhile, the liquid spraying pipeline is arranged, so that the air conditioner can select the corresponding air suction ports to be communicated according to corresponding operation working conditions, the air conditioner can reach the optimal operation state, the problem that the use temperature range of the air conditioner is limited due to high exhaust temperature is effectively solved, and the heating quantity and the heating efficiency of the air conditioner are improved.
Description
Technical Field
The invention relates to the technical field of air conditioner equipment, in particular to an air conditioner.
Background
In the prior art, an R32 air source heat pump has high exhaust temperature, and is particularly used in the hot water occasion of the heat pump, when the required water temperature is high and the outdoor environment temperature is low, the exhaust temperature is easy to exceed the protection limit temperature of a compressor, and the use temperature range of the air source heat pump is limited. The single-stage air source heat pump with liquid can reduce the exhaust temperature to a certain extent, but can reduce the heating capacity and COP of the air source heat pump. In the low pressure area of the compression cavity of the air source heat pump, liquid refrigerant which is not evaporated yet exists, and the liquid refrigerant can dilute an oil film to cause lubricating oil leakage loss, cause friction loss of a pump body structure and even cause the problem of reliability of operation of the air conditioner. The two-stage or quasi-two-stage compression middle air-supplying enthalpy-increasing technology is adopted, the exhaust temperature is reduced to a certain extent, and when liquid is supplemented to the compressor at the same time, the exhaust temperature can be further reduced, but the design of high-low pressure stage volume displacement ratio is limited, so that the reduction of the exhaust temperature is limited. In addition, the existing gas-supplying enthalpy-increasing technologies have gas-supplying mixing loss and backflow loss in different degrees, and the problems of flow resistance loss and the like in double-stage gas supplying, so that the exertion of the gas-supplying enthalpy-increasing technical effect is limited to a certain extent.
Disclosure of Invention
The invention mainly aims to provide an air conditioner, which comprises a compressor, a first heat exchanger, an air supplementing and supercooling device, a second heat exchanger and a gas-liquid separator, wherein the compressor, the first heat exchanger, the air supplementing and supercooling device, the second heat exchanger and the gas-liquid separator are communicated; the compressor comprises a pump body structure, the pump body structure comprises at least one cylinder, the cylinder comprises a main working cavity and an auxiliary working cavity, the main working cavity and the auxiliary working cavity are both provided with an air suction port and an air exhaust port, and the air suction port of the auxiliary working cavity is selectively communicated with a gas-liquid separator or an air supply supercooling device; and a first end of the liquid spraying pipeline is communicated with the first heat exchanger, and a second end of the liquid spraying pipeline is communicated with the main working cavity.
Furthermore, the main working cavities are multiple, the main working cavities are arranged in series, and the second end of the liquid spraying pipeline is arranged between every two adjacent main working cavities and communicated with one of the main working cavities.
Furthermore, a liquid spraying port is formed in the wall of the main working cavity, and the second end of the liquid spraying pipeline is communicated with the main working cavity through the liquid spraying port.
Further, the cylinder includes: the first cylinder comprises a first sliding sheet and a second sliding sheet, the first sliding sheet and the second sliding sheet separate an inner cavity of the first cylinder into a first cavity and a second cavity, the first cavity forms a main working cavity, and the second cavity forms an auxiliary working cavity.
Furthermore, the first cavity is provided with a first air suction port and a first exhaust port, the first air suction port is communicated with the gas-liquid separator, the first exhaust port is communicated with the first heat exchanger, the second cavity is provided with a second air suction port and a second exhaust port, the second air suction port is selectively communicated with the gas-liquid separator or the air supply supercooling device, and the second exhaust port is communicated with the first heat exchanger.
Further, the air cylinder comprises a second air cylinder, the second air cylinder is overlapped with the first air cylinder, the second air cylinder is provided with a third cavity, the first cavity is provided with a first air suction port and a first exhaust port, the second cavity is provided with a second air suction port and a second exhaust port, the third cavity is provided with a third air suction port and a third exhaust port, the first air suction port is communicated with the gas-liquid separator, the second exhaust port is communicated with the first heat exchanger, the second air suction port is selectively communicated with the gas-liquid separator or the air supply supercooling device, the third air suction port is communicated with the first exhaust port, and the third exhaust port is communicated with the first heat exchanger.
Furthermore, a valve is arranged on a pipeline for communicating the second air suction port with the outlet end of the gas-liquid separator.
Furthermore, the inlet end of the air supply supercooling device is communicated with the outlet end of the first heat exchanger, the outlet end of the air supply supercooling device is communicated with the inlet end of the second heat exchanger, the air supply supercooling device further comprises an auxiliary path, one end of the auxiliary path is communicated with the outlet end of the first heat exchanger, and the other end of the auxiliary path is communicated with the auxiliary working cavity.
Further, a first throttling device is arranged on the auxiliary road.
Further, a second throttling device is arranged on the liquid spraying pipeline.
Further, the pump body structure includes a plurality of cylinders, and each cylinder has a working chamber, and a plurality of cylinders set up along vertical direction.
Further, the multiple cylinders comprise a third cylinder, the third cylinder is provided with a fourth cavity, the fourth cavity is provided with a fourth air suction port and a fourth air exhaust port, the fourth air suction port is selectively communicated with the air supply supercooling device or the gas-liquid separator, and the fourth air exhaust port is communicated with the first heat exchanger.
Further, the multiple cylinders comprise a fourth cylinder and a fifth cylinder, the fourth cylinder is provided with a fifth cavity, the fifth cavity is provided with a fifth air suction port and a fifth air exhaust port, the fifth air exhaust port is communicated with the first heat exchanger, the fifth cylinder is provided with a sixth cavity, the sixth cavity is provided with a sixth air suction port and a sixth air exhaust port, the sixth air suction port is communicated with the gas-liquid separator, and the sixth air exhaust port is communicated with the fifth air suction port.
Further, the air make-up subcooling device comprises: and a liquid inlet pipeline of the flash tank is communicated with the outlet end of the first heat exchanger, a liquid outlet pipeline of the flash tank is communicated with the inlet end of the second heat exchanger, and an air outlet of the flash tank is communicated with the auxiliary working cavity.
Further, the volume ratio of the fourth cavity to the sixth cavity is Q1, wherein Q1 is more than or equal to 0.05 and less than or equal to 0.2.
Further, the volume ratio of the fifth cavity to the sixth cavity is Q2, wherein Q2 is more than or equal to 0.25 and less than or equal to 0.65.
Further, the volume ratio of the second cavity to the first cavity is Q3, wherein Q3 is more than or equal to 0.05 and less than or equal to 0.2.
Further, the volume ratio of the third cavity to the first cavity is Q4, wherein Q4 is more than or equal to 0.25 and less than or equal to 0.65.
By applying the technical scheme of the invention, the air conditioner comprises a compressor, a first heat exchanger, an air supply supercooling device, a second heat exchanger, a gas-liquid separator and a liquid spraying pipeline which are communicated. The compressor comprises a pump body structure, the pump body structure comprises at least one cylinder, the cylinder comprises a main working cavity and an auxiliary working cavity, the main working cavity and the auxiliary working cavity are respectively provided with an air suction port and an air exhaust port, and the air suction port of the auxiliary working cavity is selectively communicated with a gas-liquid separator or an air supply supercooling device. The first end of the liquid spraying pipeline is communicated with the first heat exchanger, and the second end of the liquid spraying pipeline is communicated with the main working cavity. The air suction ports of the auxiliary working cavity are selectively communicated with the gas-liquid separator or the air supply supercooling device, and meanwhile, the liquid spraying pipeline is arranged, so that the air conditioner can select the corresponding air suction ports to be communicated according to corresponding operation working conditions, the air conditioner can reach the optimal operation state, the problem that the use temperature range of the air conditioner is limited due to high exhaust temperature is effectively solved, and the heating quantity and the heating efficiency of the air conditioner are improved.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this application, illustrate embodiments of the invention and, together with the description, serve to explain the invention and not to limit the invention. In the drawings:
fig. 1 is a schematic structural view illustrating a first embodiment of a compressor cylinder of an air conditioner according to the present invention;
FIG. 2 is a schematic structural view of a second embodiment of a compressor cylinder of the air conditioner of FIG. 1;
FIG. 3 is a schematic structural view of a third embodiment of a compressor cylinder of the air conditioner of FIG. 1;
FIG. 4 is a schematic diagram of a first embodiment of a control system for the air conditioner of FIG. 1;
FIG. 5 is a schematic diagram of a second embodiment of the control system of the air conditioner of FIG. 1;
FIG. 6 is a schematic view showing a first embodiment of a compressor cylinder connection of the air conditioner of FIG. 1;
FIG. 7 is a schematic view showing a second embodiment of a compressor cylinder connection of the air conditioner of FIG. 1; and
fig. 8 is a schematic structural view illustrating a fourth embodiment of a compressor cylinder of the air conditioner of fig. 1.
Wherein the figures include the following reference numerals:
10. a compressor; 11. a first cylinder; 12. a first slip sheet; 13. a second slip sheet; 133. a liquid spraying port; 14. a second cylinder; 15. a third cylinder; 16. a fourth cylinder; 17. a fifth cylinder; 20. a first heat exchanger; 30. a gas supplementing and supercooling device; 31. a road is assisted; 32. a flash tank; 40. a second heat exchanger; 50. a pipeline; 51. a main road; 52. a branch circuit; 53. connecting a pipeline; 60. a gas-liquid separator; 71. a valve; 72. a first throttling device; 73. a second throttling device; 74. a valve; 75. a throttling device; 76. a throttling device; 80. and a liquid spraying pipeline.
Detailed Description
It should be noted that the embodiments and features of the embodiments in the present application may be combined with each other without conflict. The present invention will be described in detail below with reference to the embodiments with reference to the attached drawings.
It is noted that the terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of example embodiments according to the present application. As used herein, the singular forms "a", "an" and "the" are intended to include the plural forms as well, and it should be understood that when the terms "comprises" and/or "comprising" are used in this specification, they specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof, unless the context clearly indicates otherwise.
It should be noted that the terms "first," "second," and the like in the description and claims of this application and in the drawings described above are used for distinguishing between similar elements and not necessarily for describing a particular sequential or chronological order. It is to be understood that the terms so used are interchangeable under appropriate circumstances such that the embodiments of the application described herein are, for example, capable of operation in sequences other than those illustrated or otherwise described herein. Furthermore, the terms "comprises," "comprising," and "having," and any variations thereof, are intended to cover a non-exclusive inclusion, such that a process, method, system, article, or apparatus that comprises a list of steps or elements is not necessarily limited to those steps or elements expressly listed, but may include other steps or elements not expressly listed or inherent to such process, method, article, or apparatus.
Spatially relative terms, such as "above … …," "above … …," "above … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial relationship to another device or feature as illustrated in the figures. It will be understood that the spatially relative terms are intended to encompass different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if a device in the figures is turned over, devices described as "above" or "on" other devices or configurations would then be oriented "below" or "under" the other devices or configurations. Thus, the exemplary term "above … …" can include both an orientation of "above … …" and "below … …". The device may be otherwise variously oriented (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.
Exemplary embodiments according to the present application will now be described in more detail with reference to the accompanying drawings. These exemplary embodiments may, however, be embodied in many different forms and should not be construed as limited to only the embodiments set forth herein. It is to be understood that these embodiments are provided so that this disclosure will be thorough and complete, and will fully convey the concept of the exemplary embodiments to those skilled in the art, in the drawings, it is possible to enlarge the thicknesses of layers and regions for clarity, and the same devices are denoted by the same reference numerals, and thus the description thereof will be omitted.
Referring to fig. 1 to 8, according to an embodiment of the present invention, an air conditioner is provided.
Specifically, the air conditioner comprises a compressor 10, a first heat exchanger 20, an air supply supercooling device 30, a second heat exchanger 40, a gas-liquid separator 60 and a liquid spraying pipeline 80 which are communicated with each other. The compressor 10 includes a pump structure, the pump structure includes at least one cylinder, the cylinder includes a main working chamber and an auxiliary working chamber, the main working chamber and the auxiliary working chamber both have an air suction port and an air exhaust port, and the air suction port of the auxiliary working chamber is selectively communicated with the gas-liquid separator 60 or the air supply supercooling device 30. A first end of the liquid injection line 80 is in communication with the first heat exchanger 20 and a second end of the liquid injection line 80 is in communication with the main working chamber.
In this embodiment, the air suction ports of the auxiliary working chamber are selectively communicated with the gas-liquid separator 60 or the air supply supercooling device 30, and the liquid injection pipeline is provided, so that the air conditioner can select the corresponding air suction ports to communicate according to the corresponding operating conditions, so that the air conditioner can reach the optimal operating state, the problem that the use temperature range of the air conditioner is limited due to high exhaust temperature is effectively solved, and the heating capacity and the heating efficiency of the air conditioner are improved.
Preferably, the number of the main working chambers is multiple, the multiple main working chambers are arranged in series, and the second end of the liquid spraying pipeline 80 is arranged between two adjacent main working chambers and communicated with one of the main working chambers. The arrangement enables the main working cavity to be cooled through the liquid spraying pipeline 80, and the compression performance of the main working cavity is effectively improved.
Of course, as shown in fig. 8, a liquid spraying port 133 may be opened on the wall of one of the main working chambers, and the second end of the liquid spraying pipe 80 is communicated with the main working chamber through the liquid spraying port 133. This arrangement also serves to improve the compressibility of the main working chamber.
The cylinder includes a first cylinder 11, and cavities isolated from each other are formed in the first cylinder 11, each cavity has an air inlet (as shown in fig. 1, the air inlet 121 and the air inlet 131, and the roller 132 is located in the cylinder) and an air outlet (not shown in the figure), and a plurality of cavities form a working cavity. The structure of the air cylinder can be effectively simplified and the reliability of the operation of the compressor is improved.
The first cylinder 11 comprises a first sliding piece 12 and a second sliding piece 13, and the first sliding piece 12 and the second sliding piece 13 divide an inner cavity of the first cylinder 11 into a first cavity and a second cavity. Through setting up a plurality of gleitbretters in order to separate into a plurality of cavitys that have compression function with the cylinder inner chamber, can reduce the degree of difficulty that the cylinder was made effectively. The first cavity forms a main working cavity, the second cavity forms an auxiliary working cavity, the liquid spraying pipeline 80 is communicated with the first cavity, and the auxiliary working cavity is communicated with the second cavity.
The first cavity is provided with a first air suction port and a first exhaust port, the first air suction port is communicated with the gas-liquid separator 60, the first exhaust port is communicated with the first heat exchanger 20, the second cavity is provided with a second air suction port and a second exhaust port, the second air suction port is selectively communicated with the gas-liquid separator 60 or the air supply supercooling device 30, and the second exhaust port is communicated with the first heat exchanger 20. The arrangement can ensure that the air conditioner can be selectively communicated with the air suction port of the air cylinder or the gas-liquid separator 60 according to the actual operation working condition, and the heating capacity of the air conditioner can be effectively improved.
According to another embodiment of the present application, as shown in fig. 2, the cylinders include a second cylinder 14. The second cylinder 14 overlaps the first cylinder 11, and the second cylinder 14 has a third cavity. The first cavity is provided with a first air suction port and a first exhaust port, the second cavity is provided with a second air suction port and a second exhaust port, the third cavity is provided with a third air suction port and a third exhaust port, the first air suction port is communicated with the gas-liquid separator, the second exhaust port is communicated with the first heat exchanger, the second air suction port is selectively communicated with the gas-liquid separator or the air supply supercooling device, the third air suction port is communicated with the first exhaust port, and the third exhaust port is communicated with the first heat exchanger. The arrangement enables the second cylinder 14 to be in a normal compression state when the first cylinder 11 is in the normal compression state, and effectively avoids the problems that in the prior art, when one of the cylinders is overlapped by a plurality of cylinders and normally compressed, one of the cylinders cannot realize a normal compression mode, so that the compression friction loss is caused, and the heating capacity of the compressor and the air conditioner is reduced.
As shown in fig. 4, the air conditioner includes a duct 50, and the duct 50 includes a main path 51 and a branch path 52. A first end of the main path 51 is communicated with the air outlet of the air make-up subcooling device 30. One end of the branch 52 is communicated with the second end of the main gas supply passage 51, and the second end of the branch 52 is communicated with the second gas suction port. The arrangement enables the compressor to supplement air by sucking the refrigerant in the air-supplementing supercooling device 30, effectively reduces the exhaust temperature of the compressor, and increases the heating capacity of the compressor and the air conditioner.
The air conditioner further includes a connection line 53. One end of the connecting line 53 communicates with the second end of the main path 51, and the second end of the connecting line 53 communicates with the outlet end of the gas-liquid separator 60.
In order to control the direction of the refrigerant under different working conditions, a valve 71 is arranged on the connecting pipeline 53. That is, a valve 71 is provided in a pipe connecting the second suction port and the outlet end of the gas-liquid separator 60.
The inlet end of the air supply supercooling device 30 is communicated with the outlet end of the first heat exchanger 20, the outlet end of the air supply supercooling device 30 is communicated with the inlet end of the second heat exchanger 40, the air supply supercooling device 30 further comprises an auxiliary path 31, one end of the auxiliary path 31 is communicated with the outlet end of the first heat exchanger 20, and the other end of the auxiliary path 31 is communicated with the auxiliary working cavity. The arrangement is such that the refrigerant discharged from the outlet end of the first heat exchanger 20 enters the supplementary cooling device 30 through the bypass 31 for heat exchange. In order to facilitate control of the flow rate of the refrigerant in the sub passage 31, the sub passage 31 is provided with a first throttle device 72.
Wherein a first end of the liquid injection pipeline 80 is communicated with an outlet end of the first heat exchanger 20, and the liquid injection pipeline 80 is provided with a second throttling device 73. The arrangement is such that the refrigerant discharged from the first heat exchanger 20 can enter the cylinder through the liquid injection pipe 80 to inject liquid to reduce the discharge temperature of the compressor. The second throttling device 73 can effectively control the flow rate of the refrigerant in the liquid injection pipeline 80.
In this embodiment, the pump body structure may include a plurality of cylinders. Each cylinder has a working chamber, and a plurality of cylinders are arranged along the vertical direction. The arrangement can also achieve the effect that when the cylinder as the main compression is normally compressed, the cylinder as the auxiliary compression can also carry out the normal compression without compression friction loss, and also can improve the heating quantity and the heating efficiency of the compressor.
Wherein the plurality of cylinders includes a third cylinder, a fourth cylinder, and a fifth cylinder. The third cylinder is provided with a fourth cavity, the fourth cavity is provided with a fourth air suction port and a fourth air exhaust port, the fourth air suction port is selectively communicated with the air supply supercooling device 30 or the gas-liquid separator 60, and the fourth air exhaust port is communicated with the first heat exchanger 20. The fourth cylinder has a fifth cavity having a fifth suction port and a fifth exhaust port, the fifth exhaust port is communicated with the first heat exchanger 20, the fifth cylinder has a sixth cavity having a sixth suction port and a sixth exhaust port, the sixth suction port is communicated with the gas-liquid separator 60, and the sixth exhaust port is communicated with the fifth suction port.
Of course, the subcooling device 30 can also be configured as a flash tank 32 in this embodiment. The liquid inlet pipeline of the flash evaporator 32 is communicated with the outlet end of the first heat exchanger 20, the liquid outlet pipeline of the flash evaporator 32 is communicated with the inlet end of the second heat exchanger 40, and the air outlet of the flash evaporator 32 is communicated with the auxiliary working cavity. This arrangement can also serve as a problem of increasing the compression performance of the compressor and improving the compression efficiency of the air conditioner.
In order to further optimize the performance of the compressor, the volume ratio of the fourth cavity to the sixth cavity is set to be Q1, wherein Q1 is more than or equal to 0.05 and less than or equal to 0.2. The volume ratio of the fifth cavity to the sixth cavity is set to be Q2, wherein Q2 is more than or equal to 0.25 and less than or equal to 0.65. The volume ratio of the second cavity to the first cavity is set to be Q3, wherein Q3 is more than or equal to 0.05 and less than or equal to 0.2. The volume ratio of the third cavity to the first cavity is Q4, wherein Q4 is more than or equal to 0.25 and less than or equal to 0.65.
Specifically, the air conditioner is a parallel compression heat pump, and the parallel compression heat pump includes a compressor 10, an outdoor heat exchanger, i.e., the second heat exchanger 40, an indoor heat exchanger, i.e., the first heat exchanger 20, a supercooling device, i.e., the gas supply supercooling device 30, an auxiliary passage throttling device, i.e., the first throttling device 72, a main passage throttling device, i.e., the throttling device 75, a spray liquid throttling device, i.e., the second throttling device 73, a gas-liquid separator 60, and an electromagnetic two-way valve, i.e., the first valve 71, in a circulating refrigerant. As shown in fig. 1, 2 and 6, the compressor 10 has first, second and third compression chambers, the first compression chamber, i.e., the fifth cylinder 17 in fig. 6, having a first suction port and a first discharge port, the second compression chamber, i.e., the fourth cylinder 15 in fig. 6, having a second suction port and a second discharge port, and the third compression chamber, i.e., the third cylinder 16 in fig. 6, having a third suction port and a third discharge port. The first air intake of the compressor 10 is communicated with the outlet of the gas-liquid separator 60, the second air intake is communicated with the first air exhaust, the third air intake is sequentially communicated with the auxiliary path of the supercooling device, the auxiliary path throttling device and the indoor heat exchanger, and the second air exhaust and the third air exhaust are sequentially communicated with the main path channel of the supercooling device, the main throttling device, the outdoor heat exchanger and the inlet of the gas-liquid separator. And a third air suction port of the compressor in the parallel compression heat pump cycle is also communicated with an outlet of the gas-liquid separator through an electromagnetic two-way valve. And the refrigerant flow path can be selectively switched by the opening and closing of the electromagnetic two-way valve and the auxiliary path throttling device to realize the cycle of re-supercooling of the main path or no re-supercooling. And a second air suction port of the compressor in the parallel compression heat pump cycle is also communicated with an outlet of the indoor heat exchanger through a spray throttling device, and spray cooling and spray-free cooling of the main refrigerant in the compression process can be selectively realized through the opening and closing of the spray throttling device.
As shown in fig. 4 and 6, when the spray cooling is not needed, the spray throttling device 73 is turned off, and when the electromagnetic two-way valve 71 is turned off and the sub-path throttling device 72 is turned on, the main path re-subcooling cycle is implemented as follows: the refrigerant enters a gas-liquid separator for gas-liquid separation after being subjected to heat absorption, evaporation and gasification in an outdoor heat exchanger, low-pressure refrigerant gas enters a first compression cavity through a first air suction port and is compressed into medium-pressure superheated gas which is discharged from a first exhaust port into an intermediate cavity (with the mixing function of noise elimination and liquid spraying), the medium-pressure superheated gas enters a second compression cavity through a second air suction port and is compressed into high-pressure superheated gas which is discharged from a second exhaust port into a noise elimination cavity, the high-pressure superheated gas flows through a motor winding and is cooled and then is discharged into an indoor heat exchanger from an exhaust port of a compressor, the high-pressure superheated gas is condensed and releases heat in the indoor heat exchanger and is divided into a main path and an auxiliary path after being supercooled, the auxiliary path refrigerant is throttled by an auxiliary path throttling device to be reduced into medium-pressure two-phase refrigerant which enters an auxiliary path channel of a supercooling device to be subjected to heat absorption, evaporation and gasification, the medium-pressure refrigerant gas from the bypass channel of the supercooling device enters a third compression cavity from a third air suction port of the compressor and is compressed to high-pressure superheated gas, the high-pressure superheated gas is discharged to a silencing cavity in the compressor from a third air outlet, the high-pressure superheated gas discharged from the second compression cavity is converged in the silencing cavity and then flows through a motor winding, and finally the high-pressure superheated gas is discharged to the indoor heat exchanger from an air outlet of the compressor. At the moment, the supercooling device has a re-supercooling effect on the main path refrigerant, the specific enthalpy of the refrigerant entering the outdoor heat exchanger is reduced, so that the specific enthalpy difference of an inlet and an outlet is increased, the power consumption of the unit heating capacity of the first compression cavity and the second compression cavity is reduced, the power consumption of the unit heating capacity of the third compression cavity is lower, the volume heating capacity is higher, the heating performance coefficient and the heating capacity of the heat pump device are improved on the whole compared with those of a conventional single-stage compression heat pump device, meanwhile, the exhaust pressure of the third compression cavity is the same as that of the second compression cavity, but the exhaust temperature is lower, so that the temperature after exhaust gas mixing is reduced, and the. When the heat pump device operates under the working conditions of high condensation temperature and low evaporation temperature, the exhaust temperature exceeds the protection temperature of the compressor, the liquid spraying throttling device needs to be opened at the moment, because the outlet pressure of the indoor heat exchanger is higher than the suction pressure of the second air suction port, under the driving of pressure difference, the high-pressure supercooling refrigerant discharged by the indoor heat exchanger is throttled to the medium-pressure two-phase refrigerant by the throttling device, enters the middle cavity between the first exhaust port and the second air suction port and is mixed with the medium-pressure superheated gas discharged by the first exhaust port, the liquid refrigerant absorbs heat and is gasified, so that the suction superheat degree of the second air suction port is reduced, and the exhaust superheat degree of the second exhaust port is correspondingly. The amount of the sprayed liquid can be adjusted by adjusting the throttle opening of the sprayed liquid throttling device, so that the exhaust temperature of the compressor can be controlled to be in a target range. When the electromagnetic two-way valve is opened and the auxiliary path throttling device is closed, the main path does not have supercooling circulation, the corresponding operating condition is generally mild, the exhaust temperature is not high, and the liquid spraying throttling device is in a closed state. Different from the main path re-supercooling cycle, the low-pressure gas at the outlet of the gas-liquid separator simultaneously enters a first air suction port (a second air suction port after being compressed) and a third air suction port of the compressor, and is finally compressed to high-pressure superheated gas, and the supercooled refrigerant coming out of the indoor heat exchanger completely flows through the main path of the supercooling device. At the moment, the supercooling device does not have the secondary supercooling effect on the main path refrigerant, the third compression chamber is still in the effective compression mode, and the sliding friction loss caused by ineffective compression does not exist. Compared with a single-stage compression heat pump device, the heating performance coefficient is equivalent, and the heating quantity is effectively improved due to capacity increase.
Most working conditions of the heat pump device run in a re-supercooling mode, a few of the working conditions with high load and high pressure ratio extreme working conditions simultaneously need spray cooling operation to control exhaust temperature, and only a few of the working conditions run in a non-re-supercooling and non-spray mode, such as the initial start-up, low load and low pressure ratio mild working conditions and the like of the heat pump device. Therefore, compared with a single-stage compression heat pump device, the seasonal heating performance coefficient is improved, the heating capacity is improved under the working conditions of low temperature and ultralow temperature, and the reliable operation can be maintained under the extreme working conditions of high load and high pressure ratio. Compared with the heat pump device in the prior art, the heat pump device switching control structure is simpler and more reliable, has higher efficiency than the compressor in the non-compression mode working state in the prior art, and can overcome the problem of high exhaust temperature of R32 under extreme working conditions to maintain the reliable operation of the air conditioner.
In the present embodiment, the effective internal volume ratio of the fourth cavity, which is the third compression cavity, to the sixth cavity, which is the first compression cavity, is 0.05 to 0.2 with respect to the R32 refrigerant, and the further optimized internal volume ratio is 0.08 to 0.12. The effective internal volume ratio of the second compression cavity, namely the fifth cavity, to the first compression cavity, namely the sixth cavity, is 0.25-0.65 for R32 refrigerant, and the further optimized range is 0.4-0.55.
The auxiliary path throttling device and the liquid spraying throttling device are electronic expansion valves with valve closing functions, or throttling components with capillary tubes are connected in series with the electronic expansion valves with the valve closing functions, and the main path throttling device is an electronic expansion valve or a capillary tube and the like.
The subcooling device is an intermediate heat exchanger having two-sided refrigerant channels. The double-sided refrigerant of the subcooling device in fig. 4 is in a counterflow arrangement, but alternatively a parallel flow arrangement may be used.
The inlet end of the spray throttling device is connected between the outlet of the indoor heat exchanger and the main path inlet of the supercooling device, and can also be connected between the main path outlet of the supercooling device and the main path throttling device 75 as an alternative scheme, and the liquid proportion of the spray is higher under the same working condition in the alternative scheme, so that the throttling opening degree of the spray throttling device required for controlling the same exhaust temperature is smaller.
As shown in fig. 5, which is a system diagram of an alternative embodiment of the heat pump apparatus, unlike the preferred embodiment, the form of the subcooling device in fig. 5 is replaced by a flash evaporator form by an intermediate heat exchanger, the corresponding sub-circuit throttling device is replaced by a main circuit first throttling device, throttling device 76, the main circuit throttling device becomes a main circuit second throttling device, throttling device 75, and an electromagnetic two-way valve, valve 74, is added. In the alternative embodiment, the supercooling refrigerant from the indoor heat exchanger is throttled by the first throttling device and reduced to a medium-pressure two-phase state, the gas and the liquid in the supercooling device are separated, the separated gas enters the third compression cavity of the compressor, the separated liquid enters the first compression cavity of the compressor through the second throttling device, the outdoor heat exchanger and the gas-liquid separator, is finally compressed to high-pressure superheated refrigerant gas through the first compression cavity (the gas enters the second compression cavity after being compressed) and the third compression cavity and enters the sound attenuation cavity of the compressor, and the high-pressure superheated refrigerant gas flows through the motor winding and is discharged to the indoor heat exchanger through the exhaust port of the compressor. Closing valve 71 and opening valve 74 allows the subcooling device to subcool the main circuit refrigerant. On the contrary, when the valve 71 is opened and the valve 74 is closed, the supercooling device has no supercooling effect on the main refrigerant, and the low-pressure refrigerant gas from the gas-liquid separator simultaneously enters the first compression cavity (the second compression cavity after being compressed) and the third compression cavity of the compressor. The supercooling device of the embodiment has no heat exchange temperature difference, so that the supercooling device has a high supercooling effect when operating in a recooling mode, but also has the problems of coupling control of a throttling device, air suction and liquid entrainment of the second compression cavity and the like. The control method of the liquid jet throttling device in this alternative embodiment is the same as that of the preferred embodiment. The liquid spraying throttling device in the alternative embodiment is an electronic expansion valve with a valve closing function, the first throttling device and the second throttling device can be electronic expansion valves, capillary tubes and the like, and the electromagnetic two-way valve can also be replaced by an electromagnetic three-way valve with the same function. The supercooling device in this embodiment may be a bidirectional flash evaporator, and a necessary four-way reversing valve is added to realize a refrigeration function (generally, no spray cooling is needed, and therefore, the spray throttling device is in a normally closed state during the refrigeration operation).
Fig. 1 and 7 show an alternative embodiment of the compressor of the present invention and its connection schematic diagram, respectively, including a first compression chamber a having a first suction port, a first discharge port and a liquid ejection port, a second compression chamber B having a first slide piece and a second slide piece, respectively. The alternative embodiment of the compressor is to cancel the second compression cavity B of the three compression cavities in the original embodiment and move the position of the liquid spraying port to the first compression cavity. The connection mode of the second suction port and the second exhaust port of the second compression cavity of the alternative embodiment of the compressor and the third suction port and the third exhaust port of the third compression cavity of the original embodiment in the figures 4 and 5 of the parallel compression cycle heat pump device system is completely the same, and the effective volume ratio of the second compression cavity and the first compression cavity of the alternative embodiment is the same as the effective volume ratio of the third compression cavity and the first compression cavity of the original embodiment. The first air inlet and the first air outlet of the first compression cavity of the alternative embodiment of the compressor are connected in the parallel compression cycle heat pump device system in the attached figures 4 and 5 in the same way as the air inlet of the first compression cavity and the air outlet of the second compression cavity of the original embodiment. Therefore, the compressor alternative embodiment has the same theoretical technical effect as the original embodiment in the parallel compression cycle heat pump device, and the loss of flow pressure drop between the exhaust gas of the first stage of double-stage compression and the suction gas of the high-pressure stage in the original embodiment of the compressor is practically eliminated. In the figure, the letter C and the letter D represent outdoor unit and indoor unit areas, respectively.
The three-cylinder three-compression cavity of the original embodiment of the compressor can also be three-cylinder three-compression cavity, the single-cylinder two-compression cavity of the alternative embodiment of the compressor can also be two-cylinder two-compression cavity, namely the third compression cavity in the original embodiment and the second compression cavity in the alternative embodiment are replaced by a single cylinder with relatively small internal volume ratio, the size ratio of the three cylinders or the two cylinders after replacement is not adjusted, for example, for an R410A air source heat pump type air conditioner, the volume displacement of the first compression cavity of the frequency conversion compressor required by 3.5kW rated heat is 10cm3The volume displacement of the smaller cylinder is 1cm calculated according to the internal volume ratio of 0.13/rev。
It can be derived from the above description that in this embodiment, a double-cylinder three-compression chamber or a three-cylinder three-compression chamber, or a double-cylinder double-compression chamber or a single-cylinder double-compression chamber may be adopted, and the main refrigerant may flow through two of the three compression chambers in series, or flow through one of the double compression chambers, and the suction port of the three compression chambers or the remaining auxiliary compression chamber of the double compression chambers may be selectively connected to the outlet of the gas-liquid separator or the outlet of the auxiliary passage of the super-cooling device by switching the valve.
When the air suction port of the auxiliary compression cavity is communicated with the auxiliary path outlet of the supercooling device, the main path refrigerant is supercooled, the auxiliary compression cavity and the main compression cavity compress the auxiliary path refrigerant and the main path refrigerant in parallel, and the heating performance coefficient and the heating capacity of the heat pump device are effectively improved.
When the air suction port of the auxiliary compression cavity is communicated with the outlet of the gas-liquid separator, the main refrigerant is not supercooled, the auxiliary compression cavity is still effectively compressed, and the heating performance coefficient and the heating capacity of the heat pump device are improved.
And when the exhaust temperature exceeds the limit, controlling the amount of the spray liquid, and spraying the high-pressure supercooled liquid refrigerant into the serial middle cavity of the three compression cavities or the main compression cavity of the two compression cavities after throttling so as to control the exhaust temperature to a target value. Herein, the parallel compression means that at least two compression chambers respectively compress at least two different fluids at the same time.
From the above description, it can be seen that the above-described embodiments of the present invention achieve the following technical effects:
the exhaust temperature of the R32 heat pump is obviously reduced to widen the application temperature range of the R32 heat pump, the heating capacity and COP of the air conditioner under the ultralow temperature working condition are improved, meanwhile, the auxiliary compression cavity is in an effective compression mode through valve switching, the friction loss of the auxiliary compression cavity caused by ineffective compression is avoided, the seasonal performance coefficient of the heat pump system during wide working condition operation is improved, and the structure of the air conditioner is simplified.
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (18)
1. An air conditioner is characterized by comprising a compressor (10), a first heat exchanger (20), an air supply supercooling device (30), a second heat exchanger (40) and a gas-liquid separator (60), which are communicated with each other; wherein,
the compressor (10) comprises a pump body structure, the pump body structure comprises at least one cylinder, the cylinder comprises a main working cavity and an auxiliary working cavity, the main working cavity and the auxiliary working cavity are respectively provided with an air suction port and an air exhaust port, and the air suction port of the auxiliary working cavity is selectively communicated with the gas-liquid separator (60) or the air supply supercooling device (30);
the first end of the liquid spraying pipeline (80) is communicated with the first heat exchanger (20), and the second end of the liquid spraying pipeline (80) is communicated with the main working cavity.
2. The air conditioner according to claim 1, wherein the number of the main working chambers is plural, the plural main working chambers are arranged in series, and the second end of the liquid injection pipeline (80) is arranged between two adjacent main working chambers and communicated with one of the main working chambers.
3. The air conditioner according to claim 1, wherein a liquid spraying port (133) is formed in a wall of the main working chamber, and a second end of the liquid spraying pipeline (80) is communicated with the main working chamber through the liquid spraying port (133).
4. The air conditioner according to claim 1, wherein the cylinder comprises:
first cylinder (11), first cylinder (11) include first gleitbretter (12) and second gleitbretter (13), first gleitbretter (12) with second gleitbretter (13) will first cavity and second cavity are separated into to the inner chamber of first cylinder (11), first cavity forms main working chamber, the second cavity forms supplementary working chamber.
5. The air conditioner according to claim 4, wherein the first chamber has a first suction port communicating with the gas-liquid separator (60) and a first discharge port communicating with the first heat exchanger (20), and the second chamber has a second suction port selectively communicating with the gas-liquid separator (60) or the supplementary cooling device (30) and a second discharge port communicating with the first heat exchanger (20).
6. The air conditioner according to claim 4, wherein the cylinder includes a second cylinder (14), the second cylinder (14) is overlapped with the first cylinder (11), the second cylinder (14) has a third cavity, the first cavity has a first suction port and a first exhaust port, the second cavity has a second suction port and a second exhaust port, the third cavity has a third suction port and a third exhaust port, the first suction port is communicated with the gas-liquid separator (60), the second exhaust port is communicated with the first heat exchanger (20), the second suction port is selectively communicated with the gas-liquid separator (60) or the gas-supplementing supercooling device (30), the third suction port is communicated with the first exhaust port, and the third exhaust port is communicated with the first heat exchanger (20).
7. The air conditioner according to claim 5 or 6, wherein a valve (71) is provided on a pipe communicating the second suction port with the outlet end of the gas-liquid separator (60).
8. The air conditioner according to claim 1, wherein the inlet end of the air-supplying supercooling device (30) is communicated with the outlet end of the first heat exchanger (20), the outlet end of the air-supplying supercooling device (30) is communicated with the inlet end of the second heat exchanger (40), the air-supplying supercooling device (30) further comprises an auxiliary circuit (31), one end of the auxiliary circuit (31) is communicated with the outlet end of the first heat exchanger (20), and the other end of the auxiliary circuit (31) is communicated with the auxiliary working chamber.
9. Air conditioner according to claim 8, characterized in that said auxiliary circuit (31) is provided with a first throttling device (72).
10. Air conditioner according to claim 1, characterized in that a second throttling device (73) is arranged on the liquid injection line (80).
11. The air conditioner according to claim 1, wherein the pump body structure includes a plurality of cylinders, each of the cylinders having one working chamber, the plurality of cylinders being arranged in a vertical direction.
12. The air conditioner according to claim 11, wherein the plurality of cylinders includes a third cylinder having a fourth cavity having a fourth suction port selectively communicating with the subcooling device (30) or the gas-liquid separator (60) and a fourth discharge port communicating with the first heat exchanger (20).
13. The air conditioner according to claim 12, wherein the plurality of cylinders includes a fourth cylinder having a fifth cavity having a fifth suction port and a fifth discharge port, the fifth discharge port being in communication with the first heat exchanger (20), the fifth cylinder having a sixth cavity having a sixth suction port and a sixth discharge port, the sixth suction port being in communication with the gas-liquid separator (60), the sixth discharge port being in communication with the fifth suction port.
14. The air conditioner according to claim 1, wherein the air make-up subcooling device (30) comprises:
the liquid inlet pipeline of the flash evaporator (32) is communicated with the outlet end of the first heat exchanger (20), the liquid outlet pipeline of the flash evaporator (32) is communicated with the inlet end of the second heat exchanger (40), and the gas outlet of the flash evaporator (32) is communicated with the auxiliary working cavity.
15. The air conditioner as claimed in claim 13, wherein a volume ratio of the fourth chamber to the sixth chamber is Q1, wherein Q1 is 0.05 ≦ Q1 ≦ 0.2.
16. The air conditioner as claimed in claim 13, wherein a volume ratio of the fifth chamber to the sixth chamber is Q2, wherein Q2 is 0.25 ≦ Q2 ≦ 0.65.
17. The air conditioner as claimed in claim 4 or 6, wherein a volume ratio of the second chamber to the first chamber is Q3, wherein Q3 is 0.05 ≦ Q3 ≦ 0.2.
18. The air conditioner as claimed in claim 6, wherein a volume ratio of the third chamber to the first chamber is Q4, wherein Q4 is 0.25 ≦ Q4 ≦ 0.65.
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Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107676920A (en) * | 2017-08-24 | 2018-02-09 | 青岛海尔空调电子有限公司 | A kind of water chilling unit control method and system |
CN109209883A (en) * | 2018-11-21 | 2019-01-15 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump assembly, three cylinder compressors |
CN109595845A (en) * | 2017-09-29 | 2019-04-09 | 上海海立电器有限公司 | Fresh air conditioner system and control method |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN1957211A (en) * | 2004-05-20 | 2007-05-02 | 洋马株式会社 | Engine heat pump |
CN202326241U (en) * | 2011-10-24 | 2012-07-11 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotor vortex combined type compressor and air-conditioning system with same |
CN103954064A (en) * | 2014-04-15 | 2014-07-30 | 珠海格力电器股份有限公司 | Refrigerating device |
CN103954066A (en) * | 2014-04-15 | 2014-07-30 | 珠海格力电器股份有限公司 | Refrigerating device |
CN104101124A (en) * | 2013-04-09 | 2014-10-15 | 珠海格力电器股份有限公司 | Air conditioner |
CN104315752A (en) * | 2014-10-13 | 2015-01-28 | 广东美的暖通设备有限公司 | Heat pump system and air conditioner with heat pump system |
CN206222741U (en) * | 2016-11-29 | 2017-06-06 | 珠海格力电器股份有限公司 | air conditioner |
-
2016
- 2016-11-29 CN CN201611072447.5A patent/CN106766327A/en active Pending
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN1957211A (en) * | 2004-05-20 | 2007-05-02 | 洋马株式会社 | Engine heat pump |
CN202326241U (en) * | 2011-10-24 | 2012-07-11 | 珠海格力节能环保制冷技术研究中心有限公司 | Rotor vortex combined type compressor and air-conditioning system with same |
CN104101124A (en) * | 2013-04-09 | 2014-10-15 | 珠海格力电器股份有限公司 | Air conditioner |
CN103954064A (en) * | 2014-04-15 | 2014-07-30 | 珠海格力电器股份有限公司 | Refrigerating device |
CN103954066A (en) * | 2014-04-15 | 2014-07-30 | 珠海格力电器股份有限公司 | Refrigerating device |
CN104315752A (en) * | 2014-10-13 | 2015-01-28 | 广东美的暖通设备有限公司 | Heat pump system and air conditioner with heat pump system |
CN206222741U (en) * | 2016-11-29 | 2017-06-06 | 珠海格力电器股份有限公司 | air conditioner |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN107676920A (en) * | 2017-08-24 | 2018-02-09 | 青岛海尔空调电子有限公司 | A kind of water chilling unit control method and system |
CN107676920B (en) * | 2017-08-24 | 2021-05-25 | 青岛海尔空调电子有限公司 | Water chilling unit control method and system |
CN109595845A (en) * | 2017-09-29 | 2019-04-09 | 上海海立电器有限公司 | Fresh air conditioner system and control method |
CN109595845B (en) * | 2017-09-29 | 2021-08-03 | 上海海立电器有限公司 | Fresh air conditioning system and control method |
US11480369B2 (en) | 2017-09-29 | 2022-10-25 | Shanghai Highly Electrical Appliances Co., Ltd. | Fresh-air air conditioning system and control method |
CN109209883A (en) * | 2018-11-21 | 2019-01-15 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump assembly, three cylinder compressors |
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