CN110617219A - Compressor and air conditioning system - Google Patents
Compressor and air conditioning system Download PDFInfo
- Publication number
- CN110617219A CN110617219A CN201910995450.1A CN201910995450A CN110617219A CN 110617219 A CN110617219 A CN 110617219A CN 201910995450 A CN201910995450 A CN 201910995450A CN 110617219 A CN110617219 A CN 110617219A
- Authority
- CN
- China
- Prior art keywords
- port
- way valve
- cylinder
- compressor
- heat exchanger
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
- F04C23/001—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids of similar working principle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
-
- 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
- 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
- F25B49/00—Arrangement or mounting of control or safety devices
- F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2313/00—Compression machines, plants or systems with reversible cycle not otherwise provided for
- F25B2313/027—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means
- F25B2313/02742—Compression machines, plants or systems with reversible cycle not otherwise provided for characterised by the reversing means using two four-way valves
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
The invention provides a compressor and an air conditioning system. The compressor comprises a pump body, the pump body includes the bent axle and installs n cylinders on the bent axle, n cylinders form mutually independent first refrigerant compression passageway and second refrigerant compression passageway, n more than or equal to 2, the displacement of second refrigerant compression passageway is V1, the displacement of first refrigerant compression passageway is V2, wherein, V1: v2 is 1.5-6. The compressor can be connected with the two refrigerant circulation loops to realize double refrigeration or heating, so that the refrigeration or heating capacity of the air conditioning system is improved under the condition of reducing the load of the air conditioning system, and the problem of insufficient heating capacity of the air conditioning system in the prior art in a low-temperature environment is solved. Meanwhile, when the air conditioning system is frosted to a certain degree, one of the two independent refrigerant circulation loops operates according to the refrigeration cycle to achieve the defrosting effect, and the other system operates normally to heat to achieve the defrosting effect without stopping defrosting, so that the heating and energy-saving effects are improved.
Description
Technical Field
The invention relates to the technical field of air conditioners, in particular to a compressor and an air conditioning system.
Background
At present, when the air temperature of a household air conditioner on the market is low or below zero in winter, the air conditioner frosts, the heat exchange efficiency of an outdoor heat exchanger is gradually reduced along with the aggravation of frosting, the energy efficiency of the air conditioner is reduced, in addition, the outdoor heat exchanger needs to be defrosted when frosting reaches a certain degree, the machine needs to be stopped when defrosted, the defrosting time is generally 5-10 minutes, the heating effect is obviously reduced, the air conditioner is unstable in operation, the energy efficiency in the heating season is greatly reduced, and the requirements of energy conservation and emission reduction are not met.
Disclosure of Invention
The invention mainly aims to provide a compressor and an air conditioning system, and aims to solve the problem that the air conditioning system in the prior art is unstable in operation.
In order to achieve the above object, according to an aspect of the present invention, there is provided a compressor including a pump body including a crankshaft and n cylinders mounted on the crankshaft, the n cylinders forming a first refrigerant compression passage and a second refrigerant compression passage independent of each other, n being 2 or more, a displacement of the second refrigerant compression passage being V1, a displacement of the first refrigerant compression passage being V2, wherein V1: v2 is 1.5-6.
Further, the cylinders include a first cylinder, a second cylinder, and a third cylinder, and the first cylinder, the third cylinder, and the second cylinder are sequentially arranged along an axial direction of the crankshaft, wherein the first cylinder is disposed near a first end of the crankshaft, the second cylinder is disposed near a second end of the crankshaft, the third cylinder is located between the first cylinder and the second cylinder, a refrigerant channel of the first cylinder is communicated with a refrigerant channel of the third cylinder to form the first refrigerant compression channel, and the refrigerant channel of the second cylinder forms the second refrigerant compression channel.
Further, a first partition plate is arranged between the first cylinder and the third cylinder, and a middle channel is arranged on the first partition plate.
Further, a second partition plate and a third partition plate are arranged between the third cylinder and the second cylinder, the second partition plate is closer to the third cylinder than the third partition plate, an exhaust groove used for being communicated with an exhaust port of the third cylinder is formed in the second partition plate, the third partition plate covers the exhaust groove, and a first exhaust channel communicated with the exhaust groove is formed in the side face of the second partition plate.
Further, the compressor further comprises a first flange and a first cover plate covered by a buckle cover on the first flange, the first flange and the first cover plate are both arranged close to the first end of the crankshaft, and a transmission channel used for communicating an exhaust port of the first cylinder with the intermediate channel is arranged on the first flange.
Further, the compressor still includes first knockout and tonifying qi increase enthalpy pipe, first knockout with the induction port intercommunication of first cylinder, tonifying qi increase enthalpy pipe with transmission channel intercommunication.
Further, the compressor also comprises a second flange, and a second exhaust passage used for being communicated with an exhaust port of the second cylinder is arranged on the second flange.
Further, the compressor also comprises a second liquid separator, and the second liquid separator is communicated with the air suction port of the second cylinder.
According to another aspect of the present invention, there is provided an air conditioning system comprising a compressor, the compressor being the compressor described above.
Further, the air conditioning system further comprises a first four-way valve, a first outdoor heat exchanger, a first throttling element and a first indoor heat exchanger, wherein the first four-way valve, the first outdoor heat exchanger, the first throttling element, the first indoor heat exchanger and the first refrigerant compression channel of the compressor are connected through pipelines to form a first refrigerant circulation loop; the air conditioning system further comprises a second four-way valve, a second outdoor heat exchanger, a second throttling element and a second indoor heat exchanger, wherein the second four-way valve, the second outdoor heat exchanger, the second throttling element and the second refrigerant compression channel of the compressor are connected through a pipeline to form a second refrigerant circulation loop.
Furthermore, the first outdoor heat exchanger and the second outdoor heat exchanger are arranged side by side and provide air volume through the same first fan, and the first outdoor heat exchanger is closer to the first fan than the second outdoor heat exchanger.
Furthermore, the first indoor heat exchanger and the second indoor heat exchanger are arranged side by side and pass through a second fan, and the second indoor heat exchanger is closer to the second fan than the first indoor heat exchanger.
Further, the first four-way valve comprises a first valve port, a second valve port, a third valve port and a fourth valve port, the first valve port of the first four-way valve is connected with the first exhaust channel of the compressor, the second valve port of the first four-way valve is connected with the first outdoor heat exchanger, the third valve port of the first four-way valve is connected with the first liquid separator of the compressor, and the fourth valve port of the first four-way valve is connected with the first indoor heat exchanger; the second four-way valve comprises a first control valve port, a second control valve port, a third control valve port and a fourth control valve port, the first control valve port of the second four-way valve is connected with the second exhaust channel of the compressor, the second control valve port of the second four-way valve is connected with the second outdoor heat exchanger, the third control valve port of the second four-way valve is connected with the second liquid separator of the compressor, and the fourth control valve port of the second four-way valve is connected with the second indoor heat exchanger; when the first valve port of the first four-way valve is communicated with the fourth valve port of the first four-way valve, the second valve port of the first four-way valve is communicated with the third valve port of the first four-way valve, the first control valve port of the second four-way valve is communicated with the fourth control valve port of the second four-way valve, and the second control valve port of the second four-way valve is communicated with the third control valve port of the second four-way valve, the air conditioning system is in a dual-cycle heating mode; when the first valve port of the first four-way valve is communicated with the second valve port of the first four-way valve, the third valve port of the first four-way valve is communicated with the fourth valve port of the first four-way valve, the first control valve port of the second four-way valve is communicated with the second control valve port of the second four-way valve, and the third control valve port of the second four-way valve is communicated with the fourth control valve port of the second four-way valve, the air conditioning system is in a dual-cycle cooling mode; when the first valve port of the first four-way valve is communicated with the second valve port of the first four-way valve, the third valve port of the first four-way valve is communicated with the fourth valve port of the first four-way valve, the first control valve port of the second four-way valve is communicated with the second control valve port of the second four-way valve, and the third control valve port of the second four-way valve is communicated with the fourth control valve port of the second four-way valve, the air conditioning system is in a heating defrosting mode.
Further, air conditioning system still includes third throttling element and flash vessel, the flash vessel with first throttling element intercommunication, the flash vessel with connect between the first indoor heat exchanger third throttling element, the flash vessel with the tonifying qi of compressor increases enthalpy union coupling.
By applying the technical scheme of the invention, because the compressor in the embodiment is provided with more than 2 air cylinders, and the air cylinders can form two mutually independent refrigerant compression channels in the compressor, in the actual arrangement process, n air cylinders in the compressor can form one-stage or multi-stage compression, and the exhaust gas quantity ratio of the two mutually independent first refrigerant compression channels and the second refrigerant compression channels meets V1: v2 is 1.5 to 6, the compression grade of the second refrigerant compression channel is greater than that of the first refrigerant compression channel, thus, in the process of practical use, the compressor in this embodiment can be connected to two refrigerant circulation loops to realize dual refrigeration or heating, and can realize heating and defrosting operation, the refrigeration or heating amount of the air conditioning system is increased under the condition of reducing the load of the air conditioning system, thereby solving the problem of insufficient heating amount of the air conditioning system in the prior art in a low temperature environment, meanwhile, when the air conditioning system frosts to a certain extent, one of the two independent refrigerant circulation loops operates according to the refrigeration cycle to achieve the defrosting effect, the other system operates normally to heat, the defrosting effect is achieved without stopping, and the heating and energy saving effects 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 schematically shows a cross-sectional view of a compressor of the present invention;
figure 2 schematically shows a cross-section of the pump body of the compressor of the invention;
FIG. 3 schematically illustrates a refrigerant flow diagram of the air conditioning system of the present invention in a dual cycle refrigeration mode;
FIG. 4 is a refrigerant flow diagram schematically illustrating the air conditioning system of the present invention in a dual cycle heating mode;
FIG. 5 is a schematic view showing a refrigerant flow pattern of the air conditioning system of the present invention in a defrosting heating mode;
figure 6 schematically illustrates a pressure-enthalpy diagram for the compressor of the present invention.
Wherein the figures include the following reference numerals:
10. a compressor; 11. a housing; 111. an exhaust pipe; 12. a pump body; 121. a crankshaft; 122. a first cylinder; 123. a first separator; 124. a second separator; 1241. an exhaust groove; 125. a third cylinder; 126. a third partition plate; 127. a first flange; 1271. a transmission channel; 128. a first cover plate; 129. a second flange; 1301. a second cylinder; 13. a first liquid separator; 14. an enthalpy increasing pipe for air supply; 15. a second liquid separator; 16. a motor; 20. a first four-way valve; 21. a first valve port; 22. a second valve port; 23. a third valve port; 24. a fourth valve port; 30. a first outdoor heat exchanger; 40. a first throttling element; 50. a first indoor heat exchanger; 60. a second four-way valve; 61. a first control valve port; 62. a second control valve port; 63. a third control valve port; 64. a fourth control valve port; 70. a second outdoor heat exchanger; 80. a second throttling element; 90. a second indoor heat exchanger; 100. a third throttling element; 110. a flash evaporator; 120. a first fan; 130. and a second fan.
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 data so used is 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.
At present, when the air temperature of a household air conditioner on the market is low or below zero in winter, the air conditioner frosts, the heat exchange efficiency of an outdoor heat exchanger is gradually reduced along with the aggravation of frosting, the energy efficiency of the air conditioner is reduced, in addition, the outdoor heat exchanger needs to be defrosted when frosting reaches a certain degree, the machine needs to be stopped when defrosted, the defrosting time is generally 5-10 minutes, the heating effect is obviously reduced, the air conditioner is unstable in operation, the energy efficiency in the heating season is greatly reduced, and the requirements of energy conservation and emission reduction are not met.
In order to solve the above problems, the present invention provides a compressor 10 and an air conditioning system, and referring to fig. 1 and 2, the compressor 10 of the present invention includes a housing 11, a pump body 12, and a motor 16.
The housing 11 encloses to form an installation cavity, the pump body 12 and the motor 16 are installed in the installation cavity, and the motor 16 is in driving connection with the pump body 12, so as to compress a refrigerant inside the pump body 12.
The pump body 12 includes a crankshaft 121 and n cylinders mounted on the crankshaft 121, where the n cylinders form a first refrigerant compression channel and a second refrigerant compression channel that are independent of each other, n is greater than or equal to 2, the displacement of the second refrigerant compression channel is V1, and the displacement of the first refrigerant compression channel is V2, where V1: v2 is 1.5-6.
Because the compressor 10 in this embodiment has more than 2 cylinders, and these cylinders can form two mutually independent refrigerant compression passages inside the compressor 10, in the actual arrangement process, the n cylinders inside the compressor 10 can form one-stage or multi-stage compression, and the displacement ratio in the two mutually independent first refrigerant compression passages and second refrigerant compression passages satisfies V1: v2 is 1.5 to 6, the compression grade of the second refrigerant compression channel is greater than that of the first refrigerant compression channel, thus, in the process of practical use, the compressor 10 in this embodiment can connect two refrigerant circulation loops, realize dual refrigeration or heating, and can realize heating and defrosting operation, the refrigeration or heating amount of the air conditioning system is increased under the condition of reducing the load of the air conditioning system, the problem of insufficient heating amount of the air conditioning system in the low temperature environment in the prior art is solved, meanwhile, when the air conditioning system frosts to a certain extent, one of the two independent refrigerant circulation loops operates according to the refrigeration cycle, the defrosting effect is achieved, the other system operates normally to heat, the defrosting effect is achieved without stopping, and the heating and energy saving effects are improved.
Referring to fig. 2, in a preferred embodiment of the present invention, the cylinders include a first cylinder 122, a second cylinder 1301, and a third cylinder 125, and the first cylinder 122, the second cylinder 1301, and the third cylinder 125 are sequentially arranged along an axial direction of the crankshaft 121, wherein the first cylinder 122 is disposed near a first end of the crankshaft 121, the second cylinder 1301 is disposed near a second end of the crankshaft 121, the third cylinder 125 is disposed between the first cylinder 122 and the second cylinder 1301, a refrigerant channel of the first cylinder 122 is communicated with a refrigerant channel of the third cylinder 125 to form a first refrigerant compression channel, and a refrigerant channel of the second cylinder 1301 forms a second refrigerant compression channel.
It can be seen that, in this embodiment, the first cylinder 122 and the third cylinder 125 form a two-stage compression channel, and the second cylinder 1301 forms a single-stage compression channel, in the actual use process, the two refrigerant compression channels are respectively connected to the two heat exchangers side by side, and the heat exchanger connected to the two-stage compression channel is located on the windward side of the heat exchanger connected to the single-stage compression channel.
In this embodiment, a first partition 123 is disposed between the first cylinder 122 and the third cylinder 125, and an intermediate passage (not shown) is disposed on the first partition 123 to facilitate communication between the exhaust port of the first cylinder 122 and the intake port of the third cylinder 125.
A second clapboard 124 and a third clapboard 126 are arranged between the third cylinder 125 and the second cylinder 1301, the second clapboard 124 is closer to the third cylinder 125 than the third clapboard 126, an exhaust groove 1241 used for communicating with an exhaust port of the third cylinder 125 is arranged on the second clapboard 124, the third clapboard 126 covers the exhaust groove 1241, and a first exhaust channel communicated with the exhaust groove 1241 is arranged on the side surface of the first clapboard 123. In this embodiment, the second partition plate 124 and the third partition plate 126 are disposed between the second cylinder 1301 and the third cylinder 125, such a manner is convenient for forming the exhaust groove 1241, so as to facilitate conveying the refrigerant compressed by the first cylinder 122 and the third cylinder 125 to the corresponding heat exchanger.
Referring again to fig. 1 and 2, the compressor 10 further includes a first flange 127 and a first cover plate 128 covering the first flange 127, the first flange 127 and the first cover plate 128 are disposed near the first end of the crankshaft 121, and the first flange 127 is provided with a transfer passage 1271 for communicating the exhaust port of the first cylinder 122 with the intermediate passage of the first partition 123.
The compressor 10 further comprises a first liquid separator 13 and an air-supply enthalpy-increasing pipe 14, wherein the first liquid separator 13 is communicated with an air suction port of the first cylinder 122, and the air-supply enthalpy-increasing pipe 14 is communicated with the transmission channel 1271.
During actual operation, the refrigerant enters the first cylinder 122 from the first liquid separator 13, enters the transmission channel 1271 after being compressed by the first cylinder 122, then enters the intermediate channel on the first partition plate 123, enters the medium-temperature medium-pressure refrigerant through the air-supply enthalpy-increasing pipe 14, enters the third cylinder 125, is compressed, enters the exhaust groove 1241, and is then discharged from the first exhaust channel.
The compressor 10 of this embodiment further includes a second flange 129, and a second exhaust passage (not shown) is provided on the second flange 129 for communicating with an exhaust port of the second cylinder 1301. In actual installation, the second flange 129 in this embodiment is located above the compressor 10, the first flange 127 is located at the bottom of the compressor 10, the exhaust pipe 111 is provided on the housing 11, and the refrigerant discharged from the second exhaust channel is discharged from the exhaust pipe 111 and is conveyed to the corresponding heat exchanger for heat exchange.
The compressor 10 further includes a second liquid separator 15, and the second liquid separator 15 is communicated with the suction port of the second cylinder 1301 to facilitate the supply of the refrigerant into the second cylinder 1301.
Referring to fig. 1 to 5, according to another aspect of the present invention, there is provided an air conditioning system including a compressor 10, wherein the compressor 10 is the above-mentioned compressor 10.
The air conditioning system in this embodiment further includes a first four-way valve 20, a first outdoor heat exchanger 30, a first throttling element 40, and a first indoor heat exchanger 50, wherein the first four-way valve 20, the first outdoor heat exchanger 30, the first throttling element 40, the first indoor heat exchanger 50, and a first refrigerant compression channel of the compressor 10 are connected by a pipeline to form a first refrigerant circulation loop.
The air conditioning system further includes a second four-way valve 60, a second outdoor heat exchanger 70, a second throttling element 80, and a second indoor heat exchanger 90, wherein the second four-way valve 60, the second outdoor heat exchanger 70, and a second refrigerant compression passage of the compressor 10 are connected by a pipeline to form a second refrigerant circulation loop.
Preferably, the first outdoor heat exchanger 30 and the second outdoor heat exchanger 70 are arranged side by side and provide air volume through the same first fan 120, and the first outdoor heat exchanger 30 is closer to the first fan 120 than the second outdoor heat exchanger 70, so that not only the installation space is saved and the cost is reduced, but also the frosting speed of the second outdoor heat exchanger 70 can be reduced.
Preferably, the first indoor heat exchanger 50 and the second indoor heat exchanger 90 are arranged side by side and provide air volume through the same second fan 130, and the second indoor heat exchanger 90 is closer to the second fan 130 than the second indoor heat exchanger 90, so that not only the installation space is saved and the cost is reduced, but also the power consumption can be reduced.
The first four-way valve 20 of the present embodiment includes a first port 21, a second port 22, a third port 23, and a fourth port 24, the first port 21 of the first four-way valve 20 is connected to the first exhaust path of the compressor 10, the second port 22 of the first four-way valve 20 is connected to the first outdoor heat exchanger 30, the third port 23 of the first four-way valve 20 is connected to the first liquid separator 13 of the compressor 10, and the fourth port 24 of the first four-way valve 20 is connected to the first indoor heat exchanger 50.
The second four-way valve 60 includes a first control port 61, a second control port 62, a third control port 63, and a fourth control port 64, the first control port 61 of the second four-way valve 60 is connected to the second discharge passage of the compressor 10, the second control port 62 of the second four-way valve 60 is connected to the second outdoor heat exchanger 70, the third control port 63 of the second four-way valve 60 is connected to the second liquid separator 15 of the compressor 10, and the fourth control port 64 of the second four-way valve 60 is connected to the second indoor heat exchanger 90.
When the first port 21 of the first four-way valve 20 is communicated with the fourth port 24 of the first four-way valve 20, the second port 22 of the first four-way valve 20 is communicated with the third port 23 of the first four-way valve 20, the first control port 61 of the second four-way valve 60 is communicated with the fourth control port 64 of the second four-way valve 60, and the second control port 62 of the second four-way valve 60 is communicated with the third control port 63 of the second four-way valve 60, the air conditioning system is in a dual-cycle heating mode;
when the first port 21 of the first four-way valve 20 is in communication with the second port 22 of the first four-way valve 20, the third port 23 of the first four-way valve 20 is in communication with the fourth port 24 of the first four-way valve 20, the first control port 61 of the second four-way valve 60 is in communication with the second control port 62 of the second four-way valve 60, and the third control port 63 of the second four-way valve 60 is in communication with the fourth control port 64 of the second four-way valve 60, the air conditioning system is in a dual cycle cooling mode;
when the first port 21 of the first four-way valve 20 is in communication with the second port 22 of the first four-way valve 20, the third port 23 of the first four-way valve 20 is in communication with the fourth port 24 of the first four-way valve 20, the first control port 61 of the second four-way valve 60 is in communication with the second control port 62 of the second four-way valve 60, and the third control port 63 of the second four-way valve 60 is in communication with the fourth control port 64 of the second four-way valve 60, the air conditioning system is in a heating defrost mode.
Preferably, the air conditioning system further comprises a third throttling element 100 and a flash evaporator 110, the flash evaporator 110 is communicated with an outlet of the first throttling element 40, the third throttling element 100 is connected between the flash evaporator 110 and the first indoor heat exchanger 50, and the flash evaporator 110 is connected with the air-supplementing enthalpy-increasing pipe 14 of the compressor 10.
When the air conditioning system is operating in the dual cycle cold mode: the refrigerant in the first refrigerant circulation loop and the refrigerant in the second refrigerant circulation loop have the same flow direction and adopt refrigeration cycle. The indoor side is an evaporator, condensation water is easy to generate due to low temperature of the evaporation side, and the condensation water can increase wind resistance to influence the heat exchange efficiency of the heat exchanger. As can be seen from fig. 6, the quasi-two-stage circulation system is also superior to the single-stage circulation system in terms of air conditioning energy efficiency, so the quasi-two-stage circulation system is adopted in the second refrigerant circulation loop.
When the air conditioning system operates in the dual cycle heating mode: the refrigerant flow directions in the first refrigerant circulation loop and the second refrigerant circulation loop are the same, and heating circulation is adopted. The outdoor side is the evaporation side, and cold air passes through the two heat exchangers with different evaporation temperatures in sequence, on one hand, the heat exchanger on the outdoor windward side has good heat exchange effect and high evaporation temperature, so that the frosting process of the heat exchanger on the windward side can be relieved, the frosting thickness of the second outdoor heat exchanger 70 can be reduced, and the frosting thickness of the first outdoor heat exchanger 30 on the leeward side can also be reduced due to the blocking of the second outdoor heat exchanger 70, so that the heat conduction resistance of the heat exchanger is reduced, and the heating capacity and the system energy efficiency are improved. On the other hand, because the indoor heat exchanger of the first refrigerant circulation loop is located on the leeward side, the heat exchange effect is poor, the condensation pressure and the exhaust temperature can be increased relative to the second refrigerant circulation loop, and long-term reliable operation of the compressor 10 is not facilitated.
When the air conditioning system operates in a low-temperature heating mode:
on one hand, the air conditioning system can move in a heating and defrosting mode, the refrigerant flow directions of the first refrigerant circulation loop and the second refrigerant circulation loop are opposite, namely the first refrigerant circulation loop adopts refrigeration cycle, and the first refrigerant circulation loop is small in cylinder displacement and only needs to provide heat without frosting of a pipeline. The second refrigerant circulation loop is a normal heating circulation loop, and due to the fact that frosting is not caused, the heat exchange efficiency is high, the heating efficiency can be improved, namely, a frostless effect is achieved through heating and refrigerating double circulation, an air conditioning system does not need defrosting, the running stability of the air conditioner is improved, user experience is improved, the heating season energy efficiency is improved, and the energy saving and emission reduction benefits are achieved.
On the other hand, when no frost or little frost is formed, the normal heating mode air conditioning system is adopted for circulation, the frosting condition is monitored, after the frosting reaches a set value, the four-way valve is switched and overlapped, the hot defrosting mode air conditioning system is adopted for circulation, the defrosting is achieved without stopping, although the control is complex, the first refrigerant circulation loop can be fully utilized, and the heating energy efficiency reaches the optimal state.
In sum, the two independent refrigerant circulating systems are adopted to realize non-stop efficient defrosting, the stability of the air conditioning system is improved, and the energy efficiency of the whole air conditioning system can be effectively improved by adopting the quasi-secondary circulating system.
From the above description, it can be seen that the above-described embodiments of the present invention achieve the following technical effects:
the air conditioning system provided by the invention has the advantages that the two refrigerant circulating systems are operated according to refrigeration or heating during normal refrigeration and heating operation, when the low-temperature heating working condition is adopted, the frosting degree of the first outdoor heat exchanger is monitored, when the frosting degree reaches a set value, the frosting degree is fed back to the control processor, the first four-way valve is enabled to switch the direction, the first refrigerant circulating loop is operated according to the refrigeration cycle, the defrosting effect is achieved, meanwhile, the second refrigerant circulating loop is normally operated, the heating effect is ensured, the heating stable operation during defrosting is realized, and the energy efficiency in the heating season is improved. Meanwhile, two circulations of the air conditioner are realized in the same compressor, the space of an air conditioning system is saved, and the cost is greatly reduced.
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 (14)
1. The compressor (10) is characterized by comprising a pump body (12), wherein the pump body (12) comprises a crankshaft (121) and n cylinders mounted on the crankshaft (121), the n cylinders form a first refrigerant compression channel and a second refrigerant compression channel which are independent of each other, n is greater than or equal to 2, the displacement of the second refrigerant compression channel is V1, the displacement of the first refrigerant compression channel is V2, and V1: v2 is 1.5-6.
2. The compressor (10) of claim 1, wherein the cylinders include a first cylinder (122), a second cylinder (1301), and a third cylinder (125), the first cylinder (122), the third cylinder (125), and the second cylinder (1301) are arranged in this order in the axial direction of the crankshaft (121), wherein the first cylinder (122) is disposed proximate a first end of the crankshaft (121), the second cylinder (1301) is disposed proximate a second end of the crankshaft (121), the third cylinder (125) is located between the first cylinder (122) and the second cylinder (1301), the refrigerant channel of the first cylinder (122) is communicated with the refrigerant channel of the third cylinder (125) to form the first refrigerant compression channel, the refrigerant channel of the second cylinder (1301) forms the second refrigerant compression channel.
3. A compressor (10) as set forth in claim 2 wherein a first partition (123) is disposed between said first cylinder (122) and said third cylinder (125), said first partition (123) having an intermediate passage disposed therein.
4. A compressor (10) as set forth in claim 3, wherein a second partition plate (124) and a third partition plate (126) are disposed between the third cylinder (125) and the second cylinder (1301), the second partition plate (124) is closer to the third cylinder (125) than the third partition plate (126), a discharge groove (1241) for communicating with a discharge port of the third cylinder (125) is disposed on the second partition plate (124), the third partition plate (126) is covered on the discharge groove (1241), and a first discharge passage communicating with the discharge groove (1241) is disposed on a side surface of the second partition plate (124).
5. A compressor (10) in accordance with claim 3, wherein said compressor (10) further comprises a first flange (127) and a first cover plate (128) snap-fitted over said first flange (127), said first flange (127) and said first cover plate (128) each being disposed proximate a first end of said crankshaft (121), said first flange (127) having a transfer passage (1271) disposed thereon for communicating a discharge port of said first cylinder (122) with said intermediate passage.
6. A compressor (10) as claimed in claim 5, characterized in that said compressor (10) further comprises a first liquid separator (13) and an air-supply enthalpy-increasing pipe (14), said first liquid separator (13) being in communication with an air intake of said first cylinder (122), said air-supply enthalpy-increasing pipe (14) being in communication with said transfer channel (1271).
7. The compressor (10) of claim 2, wherein the compressor (10) further comprises a second flange (129), the second flange (129) having a second discharge passage disposed thereon for communicating with a discharge port of the second cylinder (1301).
8. The compressor (10) of claim 2, wherein the compressor (10) further comprises a second liquid separator (15), the second liquid separator (15) being in communication with the suction port of the second cylinder (1301).
9. Air conditioning system comprising a compressor (10), characterized in that the compressor (10) is a compressor (10) according to any one of claims 1 to 8.
10. The air conditioning system according to claim 9, further comprising a first four-way valve (20), a first outdoor heat exchanger (30), a first throttling element (40), and a first indoor heat exchanger (50), wherein the first four-way valve (20), the first outdoor heat exchanger (30), the first throttling element (40), the first indoor heat exchanger (50) and the first refrigerant compression passage of the compressor (10) are connected by a pipe to form a first refrigerant circulation loop;
the air conditioning system further comprises a second four-way valve (60), a second outdoor heat exchanger (70), a second throttling element (80) and a second indoor heat exchanger (90), wherein the second four-way valve (60), the second outdoor heat exchanger (70), the second throttling element (80) and the second refrigerant compression channel of the compressor (10) are connected through pipelines to form a second refrigerant circulation loop.
11. Air conditioning system according to claim 10, characterized in that said first outdoor heat exchanger (30) and said second outdoor heat exchanger (70) are arranged side by side and are supplied with air by the same first fan (120), and in that said first outdoor heat exchanger (30) is closer to said first fan (120) than said second outdoor heat exchanger (70).
12. Air conditioning system according to claim 10, characterized in that said first indoor heat exchanger (50) and said second indoor heat exchanger (90) are arranged side by side and pass through a second fan (130), and said second indoor heat exchanger (90) is closer to said second fan (130) than said first indoor heat exchanger (50).
13. The air conditioning system as claimed in claim 10, wherein the first four-way valve (20) includes a first port (21), a second port (22), a third port (23), and a fourth port (24), the first port (21) of the first four-way valve (20) is connected to the first discharge passage of the compressor (10), the second port (22) of the first four-way valve (20) is connected to the first outdoor heat exchanger (30), the third port (23) of the first four-way valve (20) is connected to the first liquid separator (13) of the compressor (10), and the fourth port (24) of the first four-way valve (20) is connected to the first indoor heat exchanger (50);
the second four-way valve (60) comprises a first control valve port, a first control valve port (61), a second control valve port (62), a third control valve port (63) and a fourth control valve port (64), the first control valve port (61) of the second four-way valve (60) is connected with a second exhaust channel of the compressor (10), the second control valve port (62) of the second four-way valve (60) is connected with the second outdoor heat exchanger (70), the third control valve port (63) of the second four-way valve (60) is connected with the second liquid separator (15) of the compressor (10), and the fourth control valve port (64) of the second four-way valve (60) is connected with the second indoor heat exchanger (90); wherein the content of the first and second substances,
when the first valve port (21) of the first four-way valve (20) is communicated with the fourth valve port (24) of the first four-way valve (20), the second valve port (22) of the first four-way valve (20) is communicated with the third valve port (23) of the first four-way valve (20), the first control valve port (61) of the second four-way valve (60) is communicated with the fourth control valve port (64) of the second four-way valve (60), and the second control valve port (62) of the second four-way valve (60) is communicated with the third control valve port (63) of the second four-way valve (60), the air conditioning system is in a dual-cycle heating mode;
when the first valve port (21) of the first four-way valve (20) is communicated with the second valve port (22) of the first four-way valve (20), the third valve port (23) of the first four-way valve (20) is communicated with the fourth valve port (24) of the first four-way valve (20), the first control valve port (61) of the second four-way valve (60) is communicated with the second control valve port (62) of the second four-way valve (60), and the third control valve port (63) of the second four-way valve (60) is communicated with the fourth control valve port (64) of the second four-way valve (60), the air conditioning system is in a dual-cycle cooling mode;
when the first port (21) of the first four-way valve (20) is communicated with the second port (22) of the first four-way valve (20), the third port (23) of the first four-way valve (20) is communicated with the fourth port (24) of the first four-way valve (20), the first control port (61) of the second four-way valve (60) is communicated with the second control port (62) of the second four-way valve (60), and the third control port (63) of the second four-way valve (60) is communicated with the fourth control port (64) of the second four-way valve (60), the air conditioning system is in a heating and defrosting mode.
14. The air conditioning system of claim 10, further comprising a third throttling element (100) and a flash evaporator (110), wherein the flash evaporator (110) is communicated with the first throttling element (40), the third throttling element (100) is connected between the flash evaporator (110) and the first indoor heat exchanger (50), and the flash evaporator (110) is connected with an air-supply enthalpy-increasing pipe (14) of the compressor (10).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910995450.1A CN110617219A (en) | 2019-10-18 | 2019-10-18 | Compressor and air conditioning system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910995450.1A CN110617219A (en) | 2019-10-18 | 2019-10-18 | Compressor and air conditioning system |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN110617219A true CN110617219A (en) | 2019-12-27 |
Family
ID=68925946
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201910995450.1A Pending CN110617219A (en) | 2019-10-18 | 2019-10-18 | Compressor and air conditioning system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN110617219A (en) |
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112880131A (en) * | 2021-01-29 | 2021-06-01 | 青岛海尔空调器有限总公司 | Method and device for defrosting control of air conditioning system and air conditioning system |
| WO2022160767A1 (en) * | 2021-01-29 | 2022-08-04 | 青岛海尔空调器有限总公司 | Defrosting control method and apparatus for air conditioning system, and air conditioning system |
| CN114877428A (en) * | 2021-02-05 | 2022-08-09 | 广东美的白色家电技术创新中心有限公司 | Multi-position reversing valve, air conditioning system and air conditioner |
| WO2022227567A1 (en) * | 2021-04-28 | 2022-11-03 | 青岛海尔空调器有限总公司 | Control method for dual compressor air conditioner |
-
2019
- 2019-10-18 CN CN201910995450.1A patent/CN110617219A/en active Pending
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112880131A (en) * | 2021-01-29 | 2021-06-01 | 青岛海尔空调器有限总公司 | Method and device for defrosting control of air conditioning system and air conditioning system |
| WO2022160767A1 (en) * | 2021-01-29 | 2022-08-04 | 青岛海尔空调器有限总公司 | Defrosting control method and apparatus for air conditioning system, and air conditioning system |
| CN114877428A (en) * | 2021-02-05 | 2022-08-09 | 广东美的白色家电技术创新中心有限公司 | Multi-position reversing valve, air conditioning system and air conditioner |
| CN114877428B (en) * | 2021-02-05 | 2023-09-19 | 广东美的白色家电技术创新中心有限公司 | Multi-position reversing valve, air conditioning system and air conditioner |
| WO2022227567A1 (en) * | 2021-04-28 | 2022-11-03 | 青岛海尔空调器有限总公司 | Control method for dual compressor air conditioner |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN110617219A (en) | Compressor and air conditioning system | |
| CN109405102B (en) | Air Conditioning System | |
| CN101644508B (en) | Multi-connected air conditioner multifunctional system for cold water and hot water | |
| CN106196684B (en) | The multi-functional multi-connected air conditioning system of three control of one kind and its control method | |
| CN108626118B (en) | Compressor and heat exchange system with same | |
| CN205641690U (en) | Double heating type combined type air conditioner system | |
| CN103388922B (en) | Dual-compressor multifunctional air source heat pump air conditioner system | |
| CN102230650A (en) | Air conditioning system with multiple heating modes | |
| CN110500804B (en) | Heat pump system and control method | |
| CN101943503B (en) | Air-conditioning refrigeration facility | |
| CN110617644A (en) | Heat exchange system, air conditioner and control method of air conditioner | |
| CN108119953A (en) | Splitting heat pump air conditioner device | |
| CN107655124B (en) | Air source heat pump system of non-interrupted heat supply of defrosting | |
| CN102788447A (en) | Heat pump air conditioning system and water dispenser | |
| CN107120757A (en) | It is a kind of to be combined the heat recovery type fresh air conditioner group constituted by three refrigerant circulations | |
| CN213480643U (en) | Heat pump system and air conditioning equipment | |
| CN211422911U (en) | Compressor and air conditioning system | |
| CN201637184U (en) | Energy-saving refrigerating house and quick-freeze tunnel refrigeration equipment thereof | |
| CN210512235U (en) | Heat pump system | |
| CN210374156U (en) | Double-evaporation-temperature heat pump system and air conditioner | |
| CN205373127U (en) | Two temperature refrigeration and heating | |
| CN108759157B (en) | One-time throttling two-stage compression heat pump system | |
| CN218179319U (en) | Defrosting device of air source heat pump | |
| CN206771795U (en) | Air-conditioning system | |
| CN213514499U (en) | Heat pump system and air conditioning equipment |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |