CN112229101B - Compressor and air conditioning system - Google Patents
Compressor and air conditioning system Download PDFInfo
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- CN112229101B CN112229101B CN202011159471.9A CN202011159471A CN112229101B CN 112229101 B CN112229101 B CN 112229101B CN 202011159471 A CN202011159471 A CN 202011159471A CN 112229101 B CN112229101 B CN 112229101B
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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
- F25B31/002—Lubrication
- F25B31/004—Lubrication oil recirculating arrangements
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/02—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat for separating lubricants from the refrigerant
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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
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/07—Details of compressors or related parts
- F25B2400/074—Details of compressors or related parts with multiple cylinders
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Abstract
The invention provides a compressor and an air conditioning system, wherein the compressor comprises a shell, a high-pressure cylinder and a low-pressure cylinder which are arranged in the shell, and the compressor also comprises: the high-pressure exhaust cavity is communicated with the high-pressure exhaust port; the cavity of the low-pressure cylinder is communicated with the cavity of the shell through the low-pressure exhaust passage; the first end of the first pipeline is communicated with the cavity of the low-pressure cylinder, and the second end of the first pipeline is communicated with an evaporator of the air conditioning system; the first end of the second pipeline is communicated with the cavity of the high-pressure cylinder; a first end of the third pipeline is communicated with the cavity of the shell, and a second end of the third pipeline is used for being communicated with the second pipeline or a condenser of the air conditioning system; and the second end of the second pipeline is communicated with the third pipeline or the evaporator of the air conditioning system. The compressor solves the problem that the two-stage enthalpy-increasing compressor in the prior art is low in energy efficiency when applied to a common working condition.
Description
Technical Field
The invention relates to the field of air conditioning systems, in particular to a compressor and an air conditioning system.
Background
The air source heat pump air conditioner has the characteristics of high efficiency, cleanness and no pollution, and has huge market demand.
At present, a conventional heat pump air conditioner uses a single-stage rolling rotor compressor, and when the air conditioner is used for heating at low temperature and cooling at high temperature, the problems of fast capacity attenuation, high exhaust temperature, poor reliability and the like can occur, and the reasons are that the pressure ratio and the pressure difference are greatly increased, and the circulation flow of a refrigerant is rapidly attenuated.
Aiming at the bottleneck problem of the industry, through long-term research and deep analysis, a solution for realizing double-stage enthalpy increase on a single rolling rotor type compressor is provided: adding a stage on the basis of single-stage compression to form double-stage compression, and increasing the limit range of pressure ratio and pressure difference; the refrigerant circulation flow of a high-pressure stage is increased through the intermediate air supplement (enthalpy increase) of two-stage throttling, the refrigeration/heating quantity is improved, and the exhaust temperature is reduced.
However, when the two-stage enthalpy-increasing compressor meeting the severe working conditions is applied to the common working conditions, the number of friction pairs under the same displacement is larger than that of a single-stage double-cylinder compressor, and the energy efficiency is lower.
Disclosure of Invention
The invention mainly aims to provide a compressor and an air conditioning system, and aims to solve the problem that a double-stage enthalpy-increasing compressor in the prior art is low in energy efficiency when applied to a common working condition.
In order to achieve the above object, according to one aspect of the present invention, there is provided a compressor including a housing, a high pressure cylinder and a low pressure cylinder provided in the housing, the compressor further including: the high-pressure exhaust cavity is communicated with the high-pressure exhaust port; the cavity of the low-pressure cylinder is communicated with the cavity of the shell through the low-pressure exhaust channel; the first end of the first pipeline is communicated with the cavity of the low-pressure cylinder, and the second end of the first pipeline is communicated with an evaporator of the air conditioning system; the first end of the second pipeline is communicated with the cavity of the high-pressure cylinder; a first end of the third pipeline is communicated with the cavity of the shell, and a second end of the third pipeline is used for being communicated with the second pipeline or a condenser of the air conditioning system; and the second end of the second pipeline is communicated with the third pipeline or the evaporator of the air conditioning system.
Further, the compressor further includes: a first end of the fourth pipeline is communicated with the high-pressure exhaust port, and a second end of the fourth pipeline is communicated with a condenser of the air conditioning system; and the first end of the fifth pipeline is communicated with the cavity of the shell, and the second end of the fifth pipeline is communicated with a flash evaporator of the air conditioning system.
Further, the compressor further includes: first flange and first baffle, first baffle clamp establish between first flange and high-pressure cylinder, form the high-pressure exhaust chamber between first flange and the first baffle, and the high-pressure exhaust port sets up on first flange or first baffle.
Furthermore, the compressor has a two-stage working mode and a double-cylinder working mode, when the compressor is in the two-stage working mode, the second pipeline is communicated with the third pipeline, so that gas exhausted from the third pipeline enters the cavity of the high-pressure cylinder through the second pipeline; when the compressor is in a double-cylinder working mode, the first pipeline is connected with the second pipeline in parallel to enable the second pipeline to be communicated with the evaporator, and the third pipeline is connected with the fourth pipeline in parallel to enable the third pipeline to be communicated with the condenser.
Further, the first pipeline comprises a first air suction pipe and a first liquid separator arranged on the first air suction pipe; and/or the second conduit comprises a second suction line and a second liquid separator arranged on the second suction line.
Further, the fifth pipeline comprises an enthalpy-increasing pipe and an enthalpy-increasing component arranged on the enthalpy-increasing pipe.
Further, the compressor further includes: the second partition plate and the third partition plate are clamped between the high-pressure cylinder and the low-pressure cylinder, a first buffer cavity is formed between the second partition plate and the third partition plate, and the first buffer cavity is communicated with the cavity of the low-pressure cylinder.
Further, the compressor further includes: second flange and muffler, second flange and muffler set up the one side of keeping away from the high pressure cylinder at the low pressure jar, form the second cushion chamber between second flange and the muffler, the second cushion chamber communicates with the cavity of low pressure jar.
Further, the compressor further includes: the high-pressure exhaust device comprises a second partition plate and a third partition plate, wherein the second partition plate and the third partition plate are clamped between a high-pressure cylinder and a low-pressure cylinder, a high-pressure exhaust cavity is formed between the second partition plate and the third partition plate, and a high-pressure exhaust port is formed in the second partition plate or the third partition plate.
According to another aspect of the invention, an air conditioning system is provided, which comprises a compressor, a condenser, a flash evaporator and an evaporator, which are sequentially communicated, wherein the compressor is the compressor.
Further, the air conditioning system further includes: the first end of the first air suction branch pipe is communicated with the second end of the first pipeline, and the evaporator is communicated with the first air suction branch pipe; the first end of the second air suction branch pipe is communicated with the second end of the second pipeline, and the second end of the first air suction branch pipe is communicated with the second end of the second air suction branch pipe, so that the second air suction branch pipe is communicated with the evaporator through the first air suction branch pipe; and the first on-off control valve is arranged on the first air suction branch pipe so as to control the on-off between the first air suction branch pipe and the second air suction branch pipe through the first on-off control valve.
Further, the air conditioning system further includes: the first end of the transition branch pipe is communicated with the second air suction branch pipe, and the second end of the transition branch pipe is communicated with the second end of the third pipeline; and the second on-off control valve is arranged on the transition branch pipe so as to control the on-off between the transition branch pipe and the second suction branch pipe through the second on-off control valve.
Further, the compressor still includes the fourth pipeline, and the first end and the high pressure gas vent intercommunication of fourth pipeline, the second end of fourth pipeline are used for communicating with air conditioning system's condenser, and air conditioning system still includes: the second end of the transition branch pipe is communicated with the second end of the third pipeline through the first exhaust branch pipe; the first end of the second exhaust branch pipe is communicated with the second end of the transition branch pipe; the first end of the third exhaust branch pipe is communicated with the fourth pipeline, and the second end of the third exhaust branch pipe, the second end of the second exhaust branch pipe and the condenser are communicated so that the air flows in the second exhaust branch pipe and the third exhaust branch pipe are converged and then flow to the condenser together; and the third on-off control valve is arranged on the second exhaust branch pipe.
Further, the compressor still includes the fourth pipeline, and the first end and the high pressure gas vent intercommunication of fourth pipeline, the second end of fourth pipeline are used for communicating with air conditioning system's condenser, and air conditioning system still includes: the first valve port of the four-way reversing valve is communicated with the second end of the first pipeline, the second valve port of the four-way reversing valve is communicated with the second end of the second pipeline, and the third valve port of the four-way reversing valve is communicated with the second end of the third pipeline; the evaporator is connected with the pipe body between the fourth broken control valve and the second end of the first pipeline; and a first valve port of the three-way valve is communicated with a fourth valve port of the four-way reversing valve, a second valve port of the three-way valve is communicated with the second end of the fourth pipeline, and a third valve port of the three-way valve is communicated with the condenser.
Furthermore, the fourth break control valve is a one-way valve, and an outlet of the one-way valve is communicated with the first valve port of the four-way reversing valve.
By applying the technical scheme, the compressor comprises a low-pressure cylinder, a high-pressure exhaust cavity, a high-pressure exhaust port, a low-pressure exhaust channel, a first pipeline, a second pipeline and a third pipeline which are arranged in a shell. The cavity of the high-pressure cylinder is communicated with the high-pressure exhaust port through the high-pressure exhaust cavity, the cavity of the low-pressure cylinder is communicated with the cavity of the shell through the low-pressure exhaust channel, the cavity of the low-pressure cylinder is communicated with an evaporator of the air conditioning system through a first pipeline, a first end of a second pipeline is communicated with the cavity of the high-pressure cylinder, and the cavity of the shell is communicated with the second pipeline or a condenser of the air conditioning system through a third pipeline. When the compressor is in a severe working condition, the second end of the second pipeline is communicated with the third pipeline so as to communicate the low-pressure exhaust channel with the air suction cavity of the high-pressure cylinder, the compressor is in a two-stage working state, the low-pressure cylinder performs one-stage compression on the refrigerant, and the high-pressure cylinder performs two-stage compression on the refrigerant; when the compressor is in a common working condition, the low-pressure exhaust channel is disconnected with the air suction cavity of the high-pressure cylinder, and the evaporator respectively supplies refrigerants to the first pipeline and the second pipeline, so that the compressor is in a single-stage double-cylinder working state. Therefore, the compressor has higher energy efficiency when working under the common working condition, and the energy efficiency is not attenuated when working under the severe working condition, so that the reliability of the compressor is improved, and the problem of lower energy efficiency when the two-stage enthalpy-increasing compressor in the prior art is applied to the common working condition is solved.
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 shows a schematic construction of a compressor according to a first embodiment of the present invention;
fig. 2 shows a schematic structural view of a pump body structure of the compressor shown in fig. 1;
FIG. 3 is a cross-sectional view of the pump body structure of FIG. 2 taken along a first direction and illustrating a refrigerant flow direction in the cross-sectional view during a dual stage operation;
FIG. 4 is a cross-sectional view of the pump structure of FIG. 2 taken along a second direction and illustrating a refrigerant flow direction in the cross-sectional view during a dual stage operation;
FIG. 5 is a sectional view of the pump body structure of FIG. 3 taken along a first direction and illustrating a refrigerant flow direction in the sectional view in a dual cylinder operation state;
FIG. 6 is a sectional view of the pump body structure of FIG. 3 taken along a second direction and illustrating a refrigerant flow direction in the sectional view in a dual cylinder operation state;
fig. 7 is a sectional view of a pump body structure of a compressor according to a second embodiment of the present invention, taken along a first direction, and a refrigerant flow direction diagram in the sectional view in a two-stage operation state;
FIG. 8 is a cross-sectional view of the pump structure of FIG. 7 taken along a second direction and illustrating the flow of refrigerant in the cross-sectional view during a dual stage operation;
FIG. 9 is a sectional view of the pump body structure of FIG. 7 taken along a first direction and illustrating a refrigerant flow direction in the sectional view in a dual cylinder operation state;
FIG. 10 is a sectional view of the pump body structure of FIG. 7 taken along a second direction and illustrating the flow of refrigerant in the sectional view during a dual cylinder operation;
fig. 11 shows a cross-sectional view of a pump body structure according to a third embodiment of the present invention along a first direction and a refrigerant flow direction diagram in the cross-sectional view in a two-stage operation state;
FIG. 12 is a sectional view of the pump body structure of FIG. 11 taken along a second direction and illustrating the flow of refrigerant in the sectional view during dual stage operation;
FIG. 13 is a sectional view of the pump body structure of FIG. 11 taken along a first direction and illustrating the flow of refrigerant in the sectional view during operation with two cylinders;
FIG. 14 is a sectional view of the pump body structure of FIG. 11 taken along a second direction and illustrating the flow of refrigerant in the sectional view during operation with two cylinders;
fig. 15 shows a cross-sectional view of a pump body structure according to a fourth embodiment of the present invention along a first direction and a refrigerant flow direction diagram in the cross-sectional view in a two-stage operation state;
FIG. 16 is a sectional view of the pump body structure of FIG. 15 taken along a second direction and illustrating the flow of refrigerant in the sectional view during dual stage operation;
FIG. 17 is a sectional view of the pump body structure of FIG. 15 taken along a first direction and illustrating the flow of refrigerant in the sectional view during a dual cylinder operation;
FIG. 18 is a sectional view of the pump body structure of FIG. 15 taken in a second direction and illustrating the coolant flow direction in the sectional view during a dual cylinder operation;
fig. 19 is a schematic view illustrating a flow direction of refrigerant in a dual-stage operation state of the air conditioning system according to the first embodiment of the present invention;
fig. 20 is a schematic view illustrating a flow direction of refrigerant in a dual cylinder operation state of the air conditioning system shown in fig. 19;
fig. 21 is a schematic view illustrating a flow direction of refrigerant in a dual-stage operation state of an air conditioning system according to a second embodiment of the present invention; and
fig. 22 is a schematic view illustrating a flow direction of a refrigerant in a dual cylinder operation state of the air conditioning system shown in fig. 21.
Wherein the figures include the following reference numerals:
1. a crankshaft; 2. a low pressure cylinder; 201. a low-pressure air suction port; 3. a high pressure cylinder; 301. a high-pressure air suction port; 4. a high pressure exhaust chamber; 401. a high pressure vent; 5. a first flange; 6. a first separator; 7. a second separator; 8. a third partition plate; 9. a second flange; 10. a housing; 11. a first pipeline; 111. a first inhalation tube; 112. a first liquid separator; 12. a second pipeline; 121. a second suction duct; 122. a second liquid separator; 13. a third pipeline; 14. a fourth pipeline; 15. a fifth pipeline; 151. an enthalpy increasing pipe; 152. an enthalpy increasing component; 16. a low pressure exhaust passage; 17. a muffler; 18. a first buffer chamber; 19. a second buffer chamber; 20. a pump body structure; 100. a compressor; 200. a condenser; 300. a flash evaporator; 400. an evaporator; 510. a first gas suction branch pipe; 511. a first on-off control valve; 520. a second branch suction pipe; 530. a transition branch pipe; 531. a second on-off control valve; 540. a first exhaust branch pipe; 550. a second exhaust branch pipe; 551. a third shutoff control valve; 560. a third exhaust branch pipe; 570. a four-way reversing valve; 580. a fourth break control valve; 590. and a three-way valve.
Detailed Description
It should be noted that, in the present application, the embodiments and features of the embodiments 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.
As shown in fig. 1 to 18, the present invention provides a compressor including a shell 10, a high pressure cylinder 3 and a low pressure cylinder 2 provided in the shell 10, the compressor further including: the high-pressure exhaust cavity 4 and the high-pressure exhaust port 401, the high-pressure cylinder 3 is communicated with the high-pressure exhaust cavity 4, and the high-pressure exhaust cavity 4 is communicated with the high-pressure exhaust port 401; the cavity of the low-pressure cylinder 2 is communicated with the cavity of the shell 10 through the low-pressure exhaust passage 16; a first end of the first pipeline 11 is communicated with the cavity of the low pressure cylinder 2, and a second end of the first pipeline 11 is used for being communicated with an evaporator 400 of an air conditioning system; a first end of the second pipeline 12 is communicated with the cavity of the high-pressure cylinder 3; a third pipeline 13, a first end of the third pipeline 13 is communicated with the cavity of the shell 10, and a second end of the third pipeline 13 is used for being communicated with the second pipeline 12 or a condenser 200 of the air conditioning system; wherein a second end of the second pipe 12 communicates with the third pipe 13 or the evaporator 400 of the air conditioning system.
The compressor of the present invention includes a low pressure cylinder 2, a high pressure cylinder 3, and a high pressure discharge chamber 4 and a high pressure discharge port 401, a low pressure discharge passage 16, a first pipe 11, a second pipe 12, and a third pipe 13, which are disposed in a casing 10. The exhaust cavity of the high-pressure cylinder 3 is communicated with a high-pressure exhaust port 401 through a high-pressure exhaust cavity 4, the cavity of the low-pressure cylinder 2 is communicated with the cavity of the shell 10 through a low-pressure exhaust passage 16, the cavity of the low-pressure cylinder 2 is communicated with an evaporator 400 of an air conditioning system through a first pipeline 11, a first end of a second pipeline 12 is communicated with the cavity of the high-pressure cylinder 3, and the cavity of the shell 10 is communicated with the second pipeline 12 or a condenser 200 of the air conditioning system through a third pipeline 13. When the compressor is in a severe working condition, the second end of the second pipeline 12 is communicated with the third pipeline 13 so as to communicate the low-pressure exhaust passage 16 with the cavity of the high-pressure cylinder 3, the compressor is in a two-stage working state, the low-pressure cylinder 2 performs one-stage compression on the refrigerant, and the high-pressure cylinder 3 performs two-stage compression on the refrigerant; when the compressor is in a normal working condition, the low-pressure exhaust passage 16 is disconnected from the suction cavity of the high-pressure cylinder 3, and the evaporator 400 respectively supplies refrigerants to the first pipeline 11 and the second pipeline 12, so that the compressor is in a single-stage double-cylinder working state. Therefore, the compressor has higher energy efficiency when working under the common working condition, and the energy efficiency is not attenuated when working under the severe working condition, so that the reliability of the compressor is improved, and the problem of lower energy efficiency when the double-stage enthalpy-increasing compressor in the prior art is applied to the common working condition is solved.
In the drawings of the present invention, arrows indicate the refrigerant flow direction.
Specifically, in fig. 3 to 18, the arrows are divided into three types, i.e., large, medium, and small, the large arrow indicates a low-pressure refrigerant, the medium arrow indicates a medium-pressure refrigerant, and the small arrow indicates a high-pressure refrigerant.
Specifically, the severe working condition refers to a working condition that the ratio of the discharge pressure and the suction pressure of the compressor or the difference between the discharge pressure and the suction pressure is large; the common working condition refers to a working condition that the ratio of the discharge pressure to the suction pressure or the difference ratio of the discharge pressure to the suction pressure of the compressor is small.
The double-stage working state is a working condition with a large ratio of exhaust pressure to suction pressure, and because the double-cylinder working state is single-stage compression, the energy efficiency ratio is reduced and the operation energy consumption is increased due to the fact that the ratio of the exhaust pressure to the suction pressure is too large; in addition, when the system is operated at low ambient temperatures, the exhaust temperature may rise significantly, possibly resulting in lubricant degradation, which is best improved by using a dual stage operating regime.
The low pressure cylinder 2 has a large displacement and can be used as a first-stage compression cylinder in a two-stage working state.
The low pressure cylinder 2 is provided with a low pressure air inlet 201 communicated with the cavity of the low pressure cylinder, and the first end of the first pipeline 11 is communicated with the low pressure air inlet 201; the high-pressure cylinder 3 is provided with a high-pressure air inlet 301 communicated with the cavity of the high-pressure cylinder 3, and the first end of the second pipeline 12 is communicated with the high-pressure air inlet 301.
Specifically, the compressor further includes: a fourth pipeline 14, a first end of the fourth pipeline 14 is communicated with the high-pressure exhaust port 401, and a second end of the fourth pipeline 14 is used for being communicated with a condenser 200 of the air conditioning system; and a fifth pipeline 15, wherein a first end of the fifth pipeline 15 is communicated with the cavity of the shell 10, and a second end of the fifth pipeline 15 is used for being communicated with a flash evaporator 300 of the air conditioning system.
As shown in the embodiments of fig. 3 to 6 and 11 to 18, the compressor further includes: the high-pressure exhaust device comprises a first flange 5 and a first partition plate 6, wherein the first partition plate 6 is clamped between the first flange 5 and the high-pressure cylinder 3, a high-pressure exhaust cavity 4 is formed between the first flange 5 and the first partition plate 6, and a high-pressure exhaust port 401 is arranged on the first flange 5 or the first partition plate 6.
The first flange 5 is provided with a high-pressure exhaust groove for forming the high-pressure exhaust cavity 4, the first partition plate 6 is provided with a high-pressure communication hole for communicating the high-pressure exhaust groove with the high-pressure cylinder 3, the high-pressure exhaust port 401 is arranged on the first flange 5, and the high-pressure exhaust port 401 is communicated with the high-pressure exhaust groove, so that the refrigerant compressed by the high-pressure cylinder 3 enters the high-pressure exhaust cavity 4 through the high-pressure communication hole and then flows out of the compressor from the high-pressure exhaust port 401.
Specifically, the compressor has a two-stage working mode and a two-cylinder working mode, when the compressor is in the two-stage working mode, the second pipeline 12 is communicated with the third pipeline 13, so that gas discharged from the third pipeline 13 enters the cavity of the high-pressure cylinder 3 through the second pipeline 12; when the compressor is in the two-cylinder operation mode, the first pipe 11 is connected in parallel with the second pipe 12 to communicate the second pipe 12 with the evaporator 400, and the third pipe 13 is connected in parallel with the fourth pipe 14 to communicate the third pipe 13 with the condenser.
When the compressor is in a two-stage working state, the second pipeline 12 is communicated with the third pipeline 13, that is, the low-pressure exhaust passage 16 is communicated with the cavity of the high-pressure cylinder 3, the refrigerant once compressed by the low-pressure cylinder 2 enters the housing 10 and flows to the second pipeline 12 through the third pipeline 13 communicated with the housing 10, and then flows into the cavity of the high-pressure cylinder 3 through the second pipeline 12, and is discharged to the condenser 200 outside the compressor after being secondarily compressed by the high-pressure cylinder 3.
When the compressor is in a double-cylinder working state, the first pipeline 11 is connected in parallel with the second pipeline 12, the third pipeline 13 is connected in parallel with the fourth pipeline 14, a refrigerant to be compressed enters the low pressure cylinder 2 and the high pressure cylinder 3 through the first pipeline 11 and the second pipeline 12 respectively, and is respectively compressed by the low pressure cylinder 2 and the high pressure cylinder 3 and then discharged to a condenser 200 outside the compressor through the third pipeline 13 and the fourth pipeline 14 respectively.
Specifically, the first pipeline 11 includes a first suction pipe 111 and a first liquid separator 112 provided on the first suction pipe 111; and/or the second line 12 comprises a second suction line 121 and a second liquid separator 122 arranged on the second suction line 121.
Specifically, the fifth pipe 15 includes an enthalpy-increasing pipe 151 and an enthalpy-increasing member 152 provided on the enthalpy-increasing pipe 151.
As in the embodiments shown in fig. 3 to 6, 15 and 18, the compressor further includes: the second partition plate 7 and the third partition plate 8 are clamped between the high-pressure cylinder 3 and the low-pressure cylinder 2, a first buffer cavity 18 is formed between the second partition plate 7 and the third partition plate 8, and the first buffer cavity 18 is communicated with the cavity of the low-pressure cylinder 2.
The second partition plate 7 and the third partition plate 8 are located between the high-pressure cylinder 3 and the low-pressure cylinder 2, the second partition plate 7 is located on one side, close to the high-pressure cylinder 3, of the third partition plate 8, a first buffer cavity 18 is formed between the second partition plate 7 and the third partition plate 8, a low-pressure exhaust groove used for forming the first buffer cavity 18 is formed in the third partition plate 8, a first communication hole which communicates the cavity of the low-pressure cylinder 2 with the first buffer cavity 18 is formed in the third partition plate 8, the first buffer cavity 18 is communicated with the interior of the shell 10 of the compressor through a low-pressure exhaust channel 16, so that a refrigerant compressed by the low-pressure cylinder 2 enters the first buffer cavity 18 through the first communication hole, and then flows out of the low-pressure exhaust channel 16 into the shell of the compressor.
As in the embodiment shown in fig. 3 to 14, the compressor further includes: second flange 9 and muffler 17, second flange 9 and muffler 17 set up in the low pressure cylinder 2 and keep away from the one side of high pressure cylinder 3, form second cushion chamber 19 between second flange 9 and the muffler 17, and second cushion chamber 19 communicates with the cavity of low pressure cylinder 2.
The second flange 9 and the muffler 17 are located on one side of the low pressure cylinder 2 far away from the high pressure cylinder 3, the muffler 17 is located on one side of the second flange 9 far away from the low pressure cylinder 2, a second buffer cavity 19 is formed between the second flange 9 and the muffler 17, a sound-absorbing cavity is arranged on the muffler 17, an opening of the sound-absorbing cavity is in butt joint with the second flange 9 to form the second buffer cavity 19, a second communication hole for communicating the cavity of the low pressure cylinder 2 with the second buffer cavity 19 is formed in the second flange 9, the second buffer cavity 19 is communicated with the inside of the shell 10 of the compressor through a low pressure exhaust passage 16, so that refrigerant compressed by the low pressure cylinder 2 enters the second buffer cavity 19 through the second communication hole, and then flows out of the low pressure exhaust passage 16 into the shell of the compressor.
As shown in the embodiment of fig. 7 and 10, the compressor further includes: the high-pressure exhaust device comprises a second partition plate 7 and a third partition plate 8, wherein the second partition plate 7 and the third partition plate 8 are clamped between the high-pressure cylinder 3 and the low-pressure cylinder 2, a high-pressure exhaust cavity 4 is formed between the second partition plate 7 and the third partition plate 8, and a high-pressure exhaust port 401 is formed in the second partition plate 7 or the third partition plate 8.
The second partition plate 7 and the third partition plate 8 are located between the high pressure cylinder 3 and the low pressure cylinder 2, the second partition plate 7 is located on one side of the third partition plate 8 close to the high pressure cylinder 3, a high pressure exhaust cavity 4 is formed between the second partition plate 7 and the third partition plate 8, a high pressure exhaust groove for forming the high pressure exhaust cavity 4 is formed in the third partition plate 8, a high pressure communication hole for communicating the high pressure exhaust groove with the high pressure cylinder 3 is formed in the second partition plate 7, a high pressure exhaust port 401 is formed in the third partition plate 8, and the high pressure exhaust port 401 is communicated with the high pressure exhaust groove, so that a refrigerant compressed by the high pressure cylinder 3 enters the high pressure exhaust cavity 4 through the high pressure communication hole and then flows out of the compressor from the high pressure exhaust port 401.
In the first embodiment of the pump body structure of the compressor of fig. 3 to 6, the first flange 5 and the first partition plate 6 located on the side of the high pressure cylinder 3 remote from the low pressure cylinder 2 constitute the high pressure discharge chamber 4, the second partition plate 7 and the third partition plate 8 located between the high pressure cylinder 3 and the low pressure cylinder 2 constitute the first cushion chamber 18, and the second flange 9 and the muffler 17 located on the side of the low pressure cylinder 2 remote from the high pressure cylinder 3 constitute the second cushion chamber 19.
Fig. 3 and 4 are schematic diagrams illustrating a flow direction of a refrigerant in a two-stage working state according to a first embodiment of a pump body structure of the compressor, at this time, the low-pressure exhaust passage 16 is communicated with a cavity of the high-pressure cylinder 3, and the refrigerant once compressed by the low-pressure cylinder 2 enters the cavity of the high-pressure cylinder 3 to be compressed for the second time and then is discharged out of the compressor; fig. 5 and 6 are schematic diagrams illustrating the flow direction of the refrigerant in the double-cylinder working state according to the first embodiment of the pump body structure of the compressor, at this time, the low-pressure exhaust passage 16 is disconnected from the cavity of the high-pressure cylinder 3, and the refrigerant in each cavity is compressed by the low-pressure cylinder 2 and the high-pressure cylinder 3 for one time and then discharged out of the compressor.
In the second embodiment of the pump body structure of the compressor of fig. 7 to 10, the second partition 7 and the third partition 8 between the high pressure cylinder 3 and the low pressure cylinder 2 constitute the high pressure discharge chamber 4, and the second flange 9 and the muffler 17 on the side of the low pressure cylinder 2 remote from the high pressure cylinder 3 constitute the second buffer chamber 19.
Fig. 7 and 8 are schematic diagrams illustrating a flow direction of a refrigerant in a two-stage working state according to the first embodiment of the pump body structure of the compressor, at this time, the low-pressure exhaust passage 16 is communicated with the cavity of the high-pressure cylinder 3, and the refrigerant once compressed by the low-pressure cylinder 2 enters the cavity of the high-pressure cylinder 3 to be compressed for the second time and then is discharged out of the compressor; fig. 9 and fig. 10 are schematic views illustrating the flow direction of the refrigerant in the double-cylinder working state according to the first embodiment of the pump structure, at this time, the low-pressure exhaust passage 16 is disconnected from the cavity of the high-pressure cylinder 3, and the refrigerant in each cavity is compressed by the low-pressure cylinder 2 and the high-pressure cylinder 3 for one time and then discharged out of the compressor.
In the third embodiment of the pump body structure of the compressor of fig. 11 to 14, the first flange 5 and the first partition plate 6 located on the side of the high pressure cylinder 3 remote from the low pressure cylinder 2 constitute the high pressure discharge chamber 4, and the second flange 9 and the muffler 17 located on the side of the low pressure cylinder 2 remote from the high pressure cylinder 3 constitute the second cushion chamber 19.
Fig. 11 and 12 are schematic diagrams illustrating a flow direction of a refrigerant in a two-stage working state according to the first embodiment of the pump body structure of the compressor, at this time, the low-pressure exhaust passage 16 is communicated with the cavity of the high-pressure cylinder 3, and the refrigerant once compressed by the low-pressure cylinder 2 enters the cavity of the high-pressure cylinder 3 to be compressed for the second time and then is discharged out of the compressor; fig. 13 and 14 are schematic diagrams illustrating the flow direction of the refrigerant in the double-cylinder working state according to the first embodiment of the pump body structure of the compressor, at this time, the low-pressure exhaust passage 16 is disconnected from the cavity of the high-pressure cylinder 3, and the refrigerant in each cavity is compressed once by the low-pressure cylinder 2 and the high-pressure cylinder 3 and then discharged out of the compressor.
In the fourth embodiment of the pump body structure of the compressor of fig. 15 to 18, the first flange 5 and the first partition plate 6 located on the side of the high pressure cylinder 3 remote from the low pressure cylinder 2 constitute the high pressure discharge chamber 4, and the second partition plate 7 and the third partition plate 8 located between the high pressure cylinder 3 and the low pressure cylinder 2 constitute the first buffer chamber 18.
Fig. 15 and 16 are schematic diagrams illustrating a flow direction of a refrigerant in a two-stage working state according to the first embodiment of the pump body structure of the compressor, at this time, the low-pressure exhaust passage 16 is communicated with the cavity of the high-pressure cylinder 3, and the refrigerant once compressed by the low-pressure cylinder 2 enters the cavity of the high-pressure cylinder 3 to be compressed for the second time and then is discharged out of the compressor; fig. 17 and 18 are schematic diagrams illustrating the flow direction of the refrigerant in the two-cylinder working state according to the first embodiment of the pump body structure of the compressor, at this time, the low-pressure exhaust passage 16 is disconnected from the cavity of the high-pressure cylinder 3, and the refrigerant in each cavity is compressed once by the low-pressure cylinder 2 and the high-pressure cylinder 3 and then discharged out of the compressor.
In the compressor of the invention, a low-pressure cylinder 2, a high-pressure cylinder 3, a first flange 5, a first clapboard 6, a second clapboard 7, a third clapboard 8, a second flange 9 and a silencer 17 are all sleeved on a crankshaft 1, and the low-pressure cylinder, the high-pressure cylinder 3, the first flange 5, the first clapboard 6, the second clapboard 7, the third clapboard 8, the second flange 9 and the silencer 17 jointly form a pump body structure 20 of the compressor.
As shown in fig. 19 to 22, the present invention further provides an air conditioning system, which includes a compressor 100, a condenser 200, a flash evaporator 300, and an evaporator 400, which are sequentially connected, wherein the compressor 100 is the above-mentioned compressor.
As shown in the embodiment of fig. 19 and 20, the air conditioning system further includes: a first suction branch pipe 510, a first end of the first suction branch pipe 510 is communicated with a second end of the first pipeline 11, and the evaporator 400 is communicated with the first suction branch pipe 510; a second branch air suction pipe 520, a first end of the second branch air suction pipe 520 being communicated with a second end of the second pipeline 12, and a second end of the first branch air suction pipe 510 being communicated with a second end of the second branch air suction pipe 520, so that the second branch air suction pipe 520 is communicated with the evaporator 400 through the first branch air suction pipe 510; a first on-off control valve 511, the first on-off control valve 511 being provided on the first branch suction pipe 510 to control the on-off between the first branch suction pipe 510 and the second branch suction pipe 520 through the first on-off control valve 511.
Specifically, the air conditioning system further includes: a branch transition pipe 530, a first end of the branch transition pipe 530 being communicated with the second branch suction pipe 520, and a second end of the branch transition pipe 530 being communicated with a second end of the third pipeline 13; a second on-off control valve 531, and a second on-off control valve 531 are provided on the transition branch pipe 530 to control the on-off between the transition branch pipe 530 and the second suction branch pipe 520 through the second on-off control valve 531.
Specifically, the compressor further includes a fourth pipeline 14, a first end of the fourth pipeline 14 is communicated with the high-pressure exhaust port 401, a second end of the fourth pipeline 14 is used for being communicated with a condenser 200 of the air conditioning system, and the air conditioning system further includes: a first exhaust branch pipe 540, a second end of the transition branch pipe 530 communicating with a second end of the third pipe 13 through the first exhaust branch pipe 540; a second exhaust branch pipe 550, a first end of the second exhaust branch pipe 550 communicating with a second end of the transition branch pipe 530; a third exhaust branch 560, a first end of the third exhaust branch 560 communicating with the fourth pipeline 14, a second end of the third exhaust branch 560, a second end of the second exhaust branch 550 and the condenser 200 communicating with each other, so that after the air flows in the second exhaust branch 550 and the third exhaust branch 560 are merged, the air flows jointly flow to the condenser 200; a third cut-off control valve 551, the third cut-off control valve 551 is provided on the second exhaust branch pipe 550.
As shown in fig. 19 and 20, the operation of the first embodiment of the air conditioning system of the present invention is as follows:
as shown in fig. 19, when the air conditioning system is in a two-stage operating state, the first on-off control valve 511 and the third on-off control valve 551 are closed, the second on-off control valve 531 is opened, the second pipeline 12 and the third pipeline 13 are communicated, the refrigerant entering the cavity of the low pressure cylinder 2 through the first pipeline 11 is subjected to one-stage compression by the low pressure cylinder 2, and then discharged into the housing 10, at this time, the housing is in a medium back pressure structure, and the refrigerant in the housing 10 flows into the cavity of the high pressure cylinder 3 through the third pipeline 13, the first exhaust branch pipe 540, the transition branch pipe 530, the second suction branch pipe 520 and the second pipeline 12, is subjected to secondary compression, and then is discharged to the condenser 200 through the fourth pipeline 14 and the third exhaust branch pipe 560.
As shown in fig. 20, when the air conditioning system is in a double-cylinder working state, the first on-off control valve 511 and the third on-off control valve 551 are opened, the second on-off control valve 531 is closed, the first pipeline 11 is connected in parallel with the second pipeline 12, the third pipeline 13 is connected in parallel with the fourth pipeline 14, a part of the refrigerant enters the low pressure cylinder 2 through the first pipeline 11, the refrigerant compressed by the low pressure cylinder 2 is discharged into the housing 10, and then flows to the condenser 200 through the third pipeline 13, the first exhaust branch pipe 540 and the second exhaust branch pipe 550; meanwhile, another part of the refrigerant enters the high pressure cylinder 3 through the first suction branch pipe 510, the second suction branch pipe 520, and the second pipeline 12, and the refrigerant compressed by the high pressure cylinder 3 is discharged to the condenser 200 through the fourth pipeline 14 and the third discharge branch pipe 560.
As shown in the embodiment of fig. 21 and 22, the compressor further includes a fourth pipeline 14, a first end of the fourth pipeline 14 is communicated with the high pressure exhaust port 401, a second end of the fourth pipeline 14 is used for being communicated with a condenser 200 of the air conditioning system, and the air conditioning system further includes: a four-way reversing valve 570, wherein a first valve port of the four-way reversing valve 570 is communicated with the second end of the first pipeline 11, a second valve port of the four-way reversing valve 570 is communicated with the second end of the second pipeline 12, and a third valve port of the four-way reversing valve 570 is communicated with the second end of the third pipeline 13; a fourth break control valve 580, the fourth break control valve 580 being provided on a pipe body between the four-way reversing valve 570 and the second end of the first pipeline 11, the evaporator 400 being connected to the pipe body between the fourth break control valve 580 and the second end of the first pipeline 11; a first port of the three-way valve 590 is connected to the fourth port of the four-way selector valve 570, a second port of the three-way valve 590 is connected to the second end of the fourth pipeline 14, and a third port of the three-way valve 590 is connected to the condenser 200.
Preferably, the fourth shutoff control valve 580 is a check valve, and an outlet of the check valve is communicated with the first port of the four-way reversing valve 570. Thus, the on-off between the first port of the four-way reversing valve 570 and the first pipeline 11 can be controlled by the check valve, so that a part of the refrigerant flowing out of the evaporator enters the first pipeline 11, the other part of the refrigerant enters from the first port of the four-way reversing valve 570 and flows out to the second pipeline 12 from the second port, and the refrigerant at the first port of the four-way reversing valve 570 cannot flow to the first pipeline 11, so as to prevent the high-pressure refrigerant from entering the low-pressure side.
As shown in fig. 21 and 22, the second embodiment of the air conditioning system of the present invention operates as follows:
as shown in fig. 21, when the air conditioning system is in a two-stage operating state, the refrigerant entering the cavity of the low pressure cylinder 2 through the first pipeline 11 is subjected to one-stage compression by the low pressure cylinder 2 and then discharged into the housing 10, at this time, the housing is in a middle back pressure structure, and the refrigerant in the housing 10 flows into the cavity of the high pressure cylinder 3 through the third pipeline 13, the four-way reversing valve 570 and the second pipeline 12 and is subjected to secondary compression, and then is discharged to the condenser 200 through the fourth pipeline 14 and the three-way valve 590.
As shown in fig. 22, when the air conditioning system is in a double-cylinder operating state, the second valve port and the third valve port of the four-way reversing valve 570 are communicated, the first pipeline 11 is connected in parallel with the second pipeline 12, the third pipeline 13 is connected in parallel with the fourth pipeline 14, a part of the refrigerant enters the low pressure cylinder 2 through the first pipeline 11, the refrigerant compressed by the low pressure cylinder 2 is discharged into the casing 10, and then flows out to the condenser 200 through the third pipeline 13, the four-way reversing valve 570 and the three-way valve 590; meanwhile, the other part of the refrigerant enters the high pressure cylinder 3 through the check valve, the four-way reversing valve 570 and the second pipeline 12, and the refrigerant compressed by the high pressure cylinder 3 is discharged to the condenser 200 through the fourth pipeline 14 and the three-way valve 590.
Specifically, in fig. 19 to 22, the solenoid valve is in a solid state, i.e., it means that the solenoid valve is open; the electromagnetic valve is in a hollow state, namely, the electromagnetic valve is closed.
From the above description, it can be seen that the above-described embodiments of the present invention achieve the following technical effects:
the compressor of the present invention includes a low pressure cylinder 2, a high pressure cylinder 3, and a high pressure discharge chamber 4 and a high pressure discharge port 401, a low pressure discharge passage 16, a first pipe 11, a second pipe 12, and a third pipe 13, which are disposed in a casing 10. The cavity of the high-pressure cylinder 3 is communicated with the high-pressure exhaust port 401 through the high-pressure exhaust cavity 4, the cavity of the low-pressure cylinder 2 is communicated with the cavity of the shell 10 through the low-pressure exhaust passage 16, the cavity of the low-pressure cylinder 2 is communicated with the evaporator 400 of the air conditioning system through the first pipeline 11, the first end of the second pipeline 12 is communicated with the cavity of the high-pressure cylinder 3, and the cavity of the shell 10 is communicated with the second pipeline 12 or the condenser 200 of the air conditioning system through the third pipeline 13.
When the compressor is in a severe working condition, the second end of the second pipeline 12 is communicated with the third pipeline 13 so as to communicate the low-pressure exhaust channel 16 with the air suction cavity of the high-pressure cylinder 3, the compressor is in a two-stage working state, the low-pressure cylinder 2 performs one-stage compression on the refrigerant, and the high-pressure cylinder 3 performs two-stage compression on the refrigerant; when the compressor is in a normal working condition, the low-pressure exhaust passage 16 is disconnected from the suction cavity of the high-pressure cylinder 3, and the evaporator 400 respectively supplies refrigerants to the first pipeline 11 and the second pipeline 12, so that the compressor is in a single-stage double-cylinder working state. Therefore, the compressor has higher energy efficiency when working under the common working condition, and the energy efficiency is not attenuated when working under the severe working condition, so that the reliability of the compressor is improved, and the problem of lower energy efficiency when the double-stage enthalpy-increasing compressor in the prior art is applied to the common working condition is solved.
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 (13)
1. Compressor comprising a casing (10), a high pressure cylinder (3) and a low pressure cylinder (2) arranged inside said casing (10), characterized in that it further comprises:
the high-pressure exhaust system comprises a high-pressure exhaust cavity (4) and a high-pressure exhaust port (401), wherein the high-pressure cylinder (3) is communicated with the high-pressure exhaust cavity (4), and the high-pressure exhaust cavity (4) is communicated with the high-pressure exhaust port (401);
the cavity of the low-pressure cylinder (2) is communicated with the cavity of the shell (10) through the low-pressure exhaust passage;
a first pipeline (11), wherein a first end of the first pipeline (11) is communicated with the cavity of the low-pressure cylinder (2), and a second end of the first pipeline (11) is used for being communicated with an evaporator (400) of an air conditioning system;
a second pipeline (12), wherein a first end of the second pipeline (12) is communicated with the cavity of the high-pressure cylinder (3);
a third pipeline (13), wherein a first end of the third pipeline (13) is communicated with the cavity of the shell (10), and a second end of the third pipeline (13) is used for being communicated with the second pipeline (12) or a condenser (200) of the air conditioning system;
a fourth pipeline (14), a first end of the fourth pipeline (14) is communicated with the high-pressure exhaust port (401), and a second end of the fourth pipeline (14) is used for being communicated with a condenser (200) of the air conditioning system;
a fifth pipeline (15), wherein a first end of the fifth pipeline (15) is communicated with the cavity of the shell (10), and a second end of the fifth pipeline (15) is used for being communicated with a flash evaporator (300) of the air conditioning system;
wherein a second end of the second conduit (12) communicates with the third conduit (13) or an evaporator (400) of the air conditioning system;
the compressor has a two-stage mode of operation and a two-cylinder mode of operation,
when the compressor is in the double-stage working mode, the second pipeline (12) is communicated with the third pipeline (13) so that gas exhausted by the third pipeline (13) enters a cavity of the high-pressure cylinder (3) through the second pipeline (12);
when the compressor is in the two-cylinder operating mode, the first line (11) is connected in parallel with the second line (12) to communicate the second line (12) with the evaporator (400), and the third line (13) is connected in parallel with the fourth line (14) to communicate the third line (13) with the condenser.
2. The compressor of claim 1, further comprising:
the high-pressure exhaust device comprises a first flange (5) and a first partition plate (6), wherein the first partition plate (6) is clamped between the first flange (5) and the high-pressure cylinder (3), the high-pressure exhaust cavity (4) is formed between the first flange (5) and the first partition plate (6), and the high-pressure exhaust port (401) is arranged on the first flange (5) or the first partition plate (6).
3. The compressor of claim 1,
the first pipeline (11) comprises a first air suction pipe (111) and a first liquid separator (112) arranged on the first air suction pipe (111); and/or
The second pipeline (12) comprises a second air suction pipe (121) and a second liquid separator (122) arranged on the second air suction pipe (121).
4. Compressor according to claim 1, characterized in that said fifth circuit (15) comprises an enthalpy-increasing pipe (151) and an enthalpy-increasing member (152) provided on said enthalpy-increasing pipe (151).
5. The compressor of claim 1, further comprising:
the hydraulic cylinder comprises a second partition plate (7) and a third partition plate (8), the second partition plate (7) and the third partition plate (8) are clamped between the high-pressure cylinder (3) and the low-pressure cylinder (2), a first buffer cavity (18) is formed between the second partition plate (7) and the third partition plate (8), and the first buffer cavity (18) is communicated with a cavity of the low-pressure cylinder (2).
6. The compressor of any one of claims 1 to 4, further comprising:
second flange (9) and muffler (17), second flange (9) with muffler (17) set up low pressure cylinder (2) are kept away from one side of high pressure cylinder (3), second flange (9) with form second cushion chamber (19) between muffler (17), second cushion chamber (19) with the cavity intercommunication of low pressure cylinder (2).
7. The compressor of claim 1, further comprising:
the high-pressure exhaust air cylinder comprises a second partition plate (7) and a third partition plate (8), the second partition plate (7) and the third partition plate (8) are clamped between the high-pressure cylinder (3) and the low-pressure cylinder (2), the high-pressure exhaust cavity (4) is formed between the second partition plate (7) and the third partition plate (8), and the high-pressure exhaust port (401) is formed in the second partition plate (7) or the third partition plate (8).
8. An air conditioning system comprising a compressor (100), a condenser (200), a flash evaporator (300) and an evaporator (400) in sequential communication, characterized in that the compressor (100) is a compressor according to any one of claims 1 to 7.
9. The air conditioning system of claim 8, further comprising:
a first branch suction pipe (510), a first end of the first branch suction pipe (510) is communicated with a second end of the first pipeline (11), and the evaporator (400) is communicated with the first branch suction pipe (510);
a second branch air suction pipe (520), a first end of the second branch air suction pipe (520) is communicated with a second end of the second pipeline (12), a second end of the first branch air suction pipe (510) is communicated with a second end of the second branch air suction pipe (520), so that the second branch air suction pipe (520) is communicated with the evaporator (400) through the first branch air suction pipe (510);
the first on-off control valve (511) is arranged on the first air suction branch pipe (510) to control the on-off between the first air suction branch pipe (510) and the second air suction branch pipe (520) through the first on-off control valve (511).
10. The air conditioning system of claim 9, further comprising:
a branch transition pipe (530), wherein a first end of the branch transition pipe (530) is communicated with the second branch suction pipe (520), and a second end of the branch transition pipe (530) is communicated with a second end of the third pipeline (13);
and the second on-off control valve (531), wherein the second on-off control valve (531) is arranged on the transition branch pipe (530) so as to control the on-off between the transition branch pipe (530) and the second suction branch pipe (520) through the second on-off control valve (531).
11. Air conditioning system according to claim 10, wherein the compressor further comprises a fourth line (14), a first end of the fourth line (14) being in communication with the high pressure discharge (401), a second end of the fourth line (14) being intended to be in communication with a condenser (200) of the air conditioning system, the air conditioning system further comprising:
a first branch exhaust pipe (540), a second end of the branch transition pipe (530) being communicated with a second end of the third pipeline (13) through the branch first exhaust pipe (540);
a second exhaust branch pipe (550), a first end of the second exhaust branch pipe (550) communicating with a second end of the transition branch pipe (530);
a third exhaust branch pipe (560), a first end of the third exhaust branch pipe (560) is communicated with the fourth pipeline (14), a second end of the third exhaust branch pipe (560), a second end of the second exhaust branch pipe (550) and the condenser (200) are communicated, so that after the air flows in the second exhaust branch pipe (550) and the third exhaust branch pipe (560) are combined, the air flows jointly flow to the condenser (200);
a third cut-off control valve (551) provided on the second exhaust branch pipe (550).
12. Air conditioning system according to claim 8, wherein the compressor further comprises a fourth line (14), a first end of the fourth line (14) being in communication with the high pressure discharge (401), a second end of the fourth line (14) being intended to be in communication with a condenser (200) of the air conditioning system, the air conditioning system further comprising:
a four-way reversing valve (570), wherein a first port of the four-way reversing valve (570) is communicated with the second end of the first pipeline (11), a second port of the four-way reversing valve (570) is communicated with the second end of the second pipeline (12), and a third port of the four-way reversing valve (570) is communicated with the second end of the third pipeline (13);
a fourth break control valve (580), the fourth break control valve (580) being disposed on a pipe between the four-way reversing valve (570) and the second end of the first pipeline (11), the evaporator (400) being connected to the pipe between the fourth break control valve (580) and the second end of the first pipeline (11);
a three-way valve (590), a first port of the three-way valve (590) is communicated with a fourth port of the four-way reversing valve (570), a second port of the three-way valve (590) is communicated with a second end of the fourth pipeline (14), and a third port of the three-way valve (590) is communicated with the condenser (200).
13. The air conditioning system of claim 12, wherein the fourth shutoff control valve (580) is a one-way valve, an outlet of the one-way valve being in communication with the first port of the four-way reversing valve (570).
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| CN112128111A (en) * | 2020-10-26 | 2020-12-25 | 珠海格力节能环保制冷技术研究中心有限公司 | Pump body structure, compressor and air conditioning system |
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