CN108444155B - Air Conditioning System - Google Patents

Air Conditioning System Download PDF

Info

Publication number
CN108444155B
CN108444155B CN201810615167.7A CN201810615167A CN108444155B CN 108444155 B CN108444155 B CN 108444155B CN 201810615167 A CN201810615167 A CN 201810615167A CN 108444155 B CN108444155 B CN 108444155B
Authority
CN
China
Prior art keywords
refrigerant
cylinder
heat exchanger
pressure
air
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN201810615167.7A
Other languages
Chinese (zh)
Other versions
CN108444155A (en
Inventor
刘星如
郑波
梁祥飞
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Gree Electric Appliances Inc of Zhuhai
Original Assignee
Gree Electric Appliances Inc of Zhuhai
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Gree Electric Appliances Inc of Zhuhai filed Critical Gree Electric Appliances Inc of Zhuhai
Priority to CN201810615167.7A priority Critical patent/CN108444155B/en
Publication of CN108444155A publication Critical patent/CN108444155A/en
Application granted granted Critical
Publication of CN108444155B publication Critical patent/CN108444155B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • 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
    • 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
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Power Engineering (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

The invention provides an air conditioning system which comprises a compressor, a first heat exchanger, a first throttling element and a second heat exchanger which are sequentially arranged on the same loop, and further comprises an unloading channel, wherein the unloading channel is connected between the compressor and the second heat exchanger to unload the compressor. The compressor and the second heat exchanger are provided with the unloading channels, the compressor is convenient to unload through the action of the unloading channels, and compared with the structure in the prior art, the air conditioning system has the advantages that the structure is simple, the compressor can be unloaded through the action of only one unloading channel, the unloading problem of the compressor under partial load is effectively solved, the compressor is ensured to always operate in a higher frequency range, and the motor efficiency and the volumetric efficiency of the compressor under small pressure ratio and low frequency are effectively improved, so that the efficiency of the air conditioning system under partial load is further improved.

Description

Air conditioning system
Technical Field
The invention relates to the technical field of air conditioners, in particular to an air conditioning system.
Background
In order to enable the air conditioner to meet the heating capacity under the least adverse working condition in winter, the existing air conditioner heat pump system generally designs the displacement of a compressor to be larger. The problem caused by the increase of the displacement of the compressor is that the indoor cooling capacity is smaller than the indoor cooling capacity under the working condition of small pressure, and the self-refrigerating and heating capacity of the air conditioner is large. In actual operation, in order to make the air-conditioning cooling and heating quantity equal to the demand, the frequency of the compressor is greatly reduced, and the volumetric efficiency and the motor efficiency of the compressor are greatly reduced due to the great reduction of the frequency, so that the performance of the compressor is greatly reduced.
To solve this problem, various scholars of the country have proposed various schemes, among which schemes of unloading and discharging are prevailing. The patent number 201610034793.8 proposes an unloading scheme for a double-rotor compressor, and the specific scheme is to switch back pressure of a sliding vane in a compressor cylinder body, so that the unloading problem of the compressor under a working condition of a small pressure ratio is solved, but the complexity and the processing difficulty of a system are greatly increased;
the 201610210434.3 patent proposes an unloading scheme for bypassing the suction cavity, which has small processing difficulty and is easy to realize, and only the back pressure of the exhaust port is required to be switched to suction pressure, but the performance is not as good as that of the suction cavity;
similarly, the solution proposed by 201610121033.0 is to connect the suction port to the discharge pressure in a manner similar to the bypass of the suction chamber, which solves the unloading problem, so that the compressor frequency remains high under small loads, but at different levels of sacrifice in performance. In addition, under the working condition of small pressure ratio, the system circulation flow is small because of small cold and heat demands, and the characteristic causes another problem that the heat exchange effect is poor.
Under normal conditions, the heat transfer resistance is mainly on the air side, and as the flow of the refrigerant decreases, the heat transfer resistance on the refrigerant side rapidly decays, in which case, the heat transfer resistance on the refrigerant side rapidly increases, and the 201520988880.8 patent proposes a system of pipelines of a recirculating evaporator, which places the gas-liquid separation at a higher height so that the liquid enters the evaporator by gravity, thereby accelerating the flow rate of the refrigerant in the evaporator, and experimental results show that the system performance is greatly improved in this way. However, this approach is structurally affected, and is not practical enough, and there is still a large room for improvement in its performance.
Disclosure of Invention
The main object of the present invention is to provide an air conditioning system to solve the problem that the compressor in the air conditioning system in the prior art is difficult to unload.
In order to achieve the above object, the present invention provides an air conditioning system including a compressor, a first heat exchanger, a first throttling element, and a second heat exchanger sequentially disposed on the same circuit, the air conditioning system further including an unloading passage connected between the compressor and the second heat exchanger to unload the compressor.
Further, the air conditioning system further comprises a second throttling element, the second throttling element is arranged on the refrigerant pipe between the first throttling element and the second heat exchanger, the first end of the unloading channel is connected with the compressor, and the second end of the unloading channel is connected on the refrigerant pipe between the first throttling element and the second throttling element or at the inlet of the second throttling element.
Further, the compressor comprises a first cylinder, an advance exhaust device is arranged on the first cylinder, the advance exhaust device is provided with an advance exhaust port and a first control valve for controlling the opening and closing of the advance exhaust port, and a first end of the unloading channel is connected with the advance exhaust port.
Further, the air conditioning system comprises a full load operation mode, when the air conditioning system is in the full load operation mode, high-temperature and high-pressure refrigerant gas is discharged from a first exhaust port on the first cylinder, is condensed into high-pressure supercooled liquid through the first heat exchanger, the high-pressure supercooled liquid is throttled into middle-pressure refrigerant through the first throttling element and then into low-temperature and low-pressure refrigerant through the second throttling element to enter the second heat exchanger, and the refrigerant is evaporated into gaseous refrigerant in the second heat exchanger and is sucked into a first air suction port of the compressor; in the full-load operating mode, the early exhaust device is always in the closed state.
Further, the air conditioning system further comprises an unloading operation mode, when the air conditioning system is in the unloading operation mode, the refrigerant coming out of the first exhaust port of the compressor is condensed into high-pressure supercooled refrigerant through the first heat exchanger, the high-pressure supercooled refrigerant is throttled to low-pressure gaseous refrigerant through the first throttling element, a first control valve on the advance exhaust device is opened, the refrigerant is discharged from the compression cavity through the advance exhaust device, the refrigerant is mixed with the refrigerant throttled by the first throttling element through the unloading channel and then enters the second heat exchanger, and the refrigerant is sucked in from the first air suction port of the compressor after being evaporated by the second heat exchanger.
Further, the compressor comprises a first cylinder and a second cylinder, the first cylinder comprises a first air suction port and a first exhaust port, the second cylinder comprises a second air suction port and a second exhaust port, the first air suction port and the second air suction port are both connected with an outlet of the second heat exchanger, and the second exhaust port is connected with an inlet of the first heat exchanger through a refrigerant pipe; the unloading channel comprises a main pipeline, a first branch and a second branch, wherein the first end of the main pipeline is connected with the second exhaust port of the second cylinder, the second end of the main pipeline is connected with the first end of the first branch and the first end of the second branch, the second end of the first branch is connected with a pipeline between the first throttling element and the second throttling element, and the second end of the second branch is connected with an inlet of the first heat exchanger; the first branch is provided with a second control valve, and the second branch is provided with a third control valve.
Further, the air conditioning system comprises a double-cylinder operation mode, when the air conditioning system is in the double-cylinder operation mode, the second control valve of the compressor is closed, the third control valve is opened, the refrigerant is discharged from the second exhaust port and the first exhaust port, the refrigerant of the second cylinder is mixed with the refrigerant of the first cylinder through the third control valve and then enters the first heat exchanger, the refrigerant is condensed into high-pressure supercooled liquid in the first heat exchanger, the high-pressure refrigerant is changed into low-temperature low-pressure refrigerant through the first throttling element and enters the second heat exchanger, the two-phase low-temperature refrigerant is evaporated into superheated steam in the second heat exchanger and is sucked into the first air suction port and the second air suction port.
Further, the air conditioning system further comprises a single-cylinder operation mode, when the air conditioning system is in the single-cylinder operation mode, the second control valve of the compressor is opened, the third control valve is closed, all the high-temperature and high-pressure refrigerant entering the first heat exchanger is from the first cylinder, the refrigerant is condensed into high-pressure supercooled refrigerant in the first heat exchanger and throttled into low-temperature and low-pressure two-phase refrigerant through the first throttling element, when the pressure in the compression cavity of the second cylinder is larger than the back pressure, the refrigerant is discharged from the second exhaust port and mixed with the low-temperature and low-pressure refrigerant throttled through the first throttling element to enter the second heat exchanger, and the refrigerant is sucked in by the first air suction port and the second air suction port after being evaporated in the second heat exchanger.
Further, the compressor comprises a first cylinder and a second cylinder, the air conditioning system is further provided with a gas-liquid separator, the first cylinder is provided with an advance exhaust device, the first cylinder comprises a first air suction port and a first exhaust port, the second cylinder comprises a second air suction port and a second exhaust port, the first air suction port is connected with an outlet of the second heat exchanger, the second exhaust port and the first exhaust port are both connected with an inlet of the first heat exchanger, the advance exhaust device comprises an advance exhaust port and a first control valve for controlling the opening and closing of the advance exhaust port, the advance exhaust port is connected with the second air suction port through a pipeline, a first end of the unloading channel and a pipeline between the advance exhaust port and the second air suction port are connected, a second end of the unloading channel is connected with a top outlet of the gas-liquid separator, an outlet of the first throttling element is connected with an inlet of the gas-liquid separator, and an inlet of the second throttling element is connected with a bottom outlet of the gas-liquid separator.
Further, when the air conditioning system is in the enthalpy-increasing operation mode, the refrigerant discharged from the first cylinder and the second cylinder of the compressor is mixed and then enters the first heat exchanger, the refrigerant is condensed into high-pressure supercooled refrigerant in the first heat exchanger, the high-pressure supercooled refrigerant is throttled into medium-pressure two-phase refrigerant by the first throttling element and enters the gas-liquid separator, in the gas-liquid separator, the liquid refrigerant enters the second throttling element through the bottom outlet of the gas-liquid separator and is throttled into low-temperature low-pressure refrigerant, and then enters the second heat exchanger to be evaporated into low-pressure superheated refrigerant, and finally is sucked by the first cylinder of the compressor; and the gaseous refrigerant in the gas-liquid separator flows out from a top outlet at the top of the gas-liquid separator and is sucked by the second air suction port, and the advance exhaust port is always in a closed state in the enthalpy-increasing operation mode.
Further, the air conditioning system further comprises an unloading operation mode, when the air conditioning system is in the unloading operation mode, the second throttling element is fully opened, high-temperature and high-pressure refrigerant discharged from the first air cylinder and the second air cylinder is condensed into high-pressure supercooled liquid through the first heat exchanger, and the high-pressure supercooled liquid enters the first throttling element to be throttled into low-pressure and low-temperature two-phase refrigerant, and enters the gas-liquid separator; when the pressure in a compression cavity of a first cylinder of the compressor is larger than the pressure in the gas-liquid separator, a first control valve of the advanced exhaust device arranged on the first cylinder is opened, the refrigerant in the first cylinder is discharged through the advanced exhaust port, the discharged refrigerant is divided into two paths, one path enters the second cylinder, the other path enters the second heat exchanger after being mixed with the low-temperature low-pressure two-phase refrigerant throttled by the first throttling element through the gas-liquid separator, the low-temperature two-phase refrigerant is evaporated into low-temperature overheated refrigerant in the second heat exchanger, and finally is sucked by the first air suction port.
Further, the compressor comprises a first air cylinder and a second air cylinder, the air conditioning system is further provided with a gas-liquid separator, the first air cylinder comprises a first air suction port and a first air exhaust port, the second air cylinder comprises a second air suction port and a second air exhaust port, the first air suction port is connected with an outlet of the second heat exchanger, the first air exhaust port is connected with an inlet of the second air suction port, the second air exhaust port is connected with an inlet of the first heat exchanger, a first end of the unloading channel is connected with a pipeline between the first air exhaust port and the second air suction port, a second end of the unloading channel is connected with a top outlet of the gas-liquid separator, an outlet of the first throttling element is connected with an inlet of the gas-liquid separator, and an inlet of the second throttling element is connected with a bottom outlet of the gas-liquid separator.
Further, the air conditioning system comprises a two-stage operation mode, when the air conditioning system is in the two-stage operation mode, high-temperature and high-pressure refrigerant discharged from the second cylinder of the compressor is condensed into high-pressure supercooled liquid through the first heat exchanger, and supercooled refrigerant discharged from the first heat exchanger is throttled to medium-pressure two-phase refrigerant through the first throttling element to enter the gas-liquid separator; in the gas-liquid separator, the refrigerant is divided into two paths, wherein liquid refrigerant flows out from the bottom outlet of the gas-liquid separator, is changed into low-temperature low-pressure refrigerant through the second throttling element and enters the second heat exchanger, and is evaporated in the second heat exchanger to be changed into low-pressure superheated refrigerant to be sucked by the first cylinder; the other path of refrigerant gas in the gas-liquid separator flows out from the top outlet at the top of the gas-liquid separator, is mixed with the refrigerant discharged by the first air cylinder and is sucked by the second air suction port, so that the cycle is completed.
Further, the air conditioning system further comprises a single-stage operation mode, when the air conditioning system is in the single-stage operation mode, the second throttling element is fully opened, the refrigerant discharged from the second air cylinder is condensed into supercooled liquid through the first heat exchanger, throttled into low-temperature low-pressure refrigerant through the first throttling element and enters the gas-liquid separator, when the pressure in the compression cavity of the first air cylinder is larger than the pressure of the gas-liquid separator, the refrigerant in the first air cylinder is discharged, the discharged refrigerant is divided into two parts, one part is sucked by the second air suction port, the other part is mixed with the low-temperature low-pressure two-phase refrigerant throttled by the first throttling element and enters the second heat exchanger, the refrigerant is evaporated into low-pressure overheat refrigerant in the second heat exchanger, and finally sucked by the first air suction port.
Further, the compressor comprises a first cylinder, a second cylinder and a third cylinder, the air conditioning system further comprises a gas-liquid separator, the first cylinder comprises a first air suction port and a first air discharge port, the second cylinder comprises a second air suction port and a second air discharge port, the third cylinder comprises a third air suction port and a third air discharge port, the first air suction port and the third air suction port are both connected with an outlet of the second heat exchanger, the first air discharge port and the third air discharge port are both connected with the second air suction port, and the second air discharge port is connected with an inlet of the first heat exchanger; the first end of the unloading channel is connected with a pipeline between the first air outlet and the second air suction port and a pipeline between the third air outlet and the second air suction port, the second end of the unloading channel is connected with the top outlet of the gas-liquid separator, the outlet of the first throttling element is connected with the inlet of the gas-liquid separator, and the inlet of the second throttling element is connected with the bottom outlet of the gas-liquid separator.
Further, the air conditioning system includes a three-cylinder two-stage operation mode, when the air conditioning system is in the three-cylinder two-stage operation mode, the first cylinder and the third cylinder suck the refrigerant from the outlet of the second heat exchanger, discharge the compressed refrigerant from the first exhaust port and the third exhaust port, mix the refrigerant discharged from the first cylinder and the third cylinder with the medium-pressure refrigerant entering the compressor from the gas-liquid separator, and suck the mixed refrigerant together with the second cylinder; the high-temperature and high-pressure refrigerant discharged from the second cylinder is condensed into high-pressure supercooled refrigerant through the first heat exchanger, and the supercooled refrigerant is throttled into medium-pressure two-phase refrigerant through the first throttling element to enter the gas-liquid separator; in the gas-liquid separator, the refrigerant is divided into two paths, and the gaseous refrigerant is sucked by the second cylinder after being mixed with the refrigerant discharged by the first cylinder and the third cylinder through the top outlet of the gas-liquid separator; the liquid refrigerant flows out from the bottom outlet of the gas-liquid separator, is throttled into low-temperature low-pressure refrigerant by the second throttling element and enters the second heat exchanger, and is evaporated into low-pressure superheated refrigerant in the second heat exchanger to be sucked by the first air suction port and the third air suction port.
Further, the air conditioning system further comprises a single-cylinder unloading operation mode, when the air conditioning system is in the single-cylinder unloading operation mode, the second throttling element is fully opened, the refrigerant discharged from the first air cylinder and the third air cylinder is divided into two parts, one part is sucked by the second air cylinder, and the other part enters the gas-liquid separator; the high-temperature and high-pressure refrigerant discharged from the second cylinder is condensed into high-pressure supercooled liquid through the first heat exchanger, and the supercooled refrigerant is throttled into low-pressure and low-temperature two-phase refrigerant through the first throttling element to enter the gas-liquid separator; in the gas-liquid separator, the low-temperature low-pressure refrigerant throttled by the first throttling element enters the second heat exchanger through the second throttling element, and in the second heat exchanger, the refrigerant evaporates into low-pressure superheated refrigerant, and is finally sucked in by the first suction port and the third suction port.
Further, the compressor comprises a first cylinder, a second cylinder, a third cylinder and a gas-liquid separator, wherein the first cylinder comprises a first air suction port and a first air discharge port, the second cylinder comprises a second air suction port and a second air discharge port, the third cylinder comprises a third air suction port and a third air discharge port, the first air suction port and the third air suction port are both connected with an outlet of the second heat exchanger, the first air discharge port and the third air discharge port are connected with the second air suction port, and the second air discharge port is connected with an inlet of the first heat exchanger; the unloading channel comprises a main pipeline, a first branch and a second branch, wherein the first end of the main pipeline is connected with the third exhaust port of the third cylinder, and the second end of the main pipeline is connected with the first end of the first branch and the first end of the second branch; the second end of the first branch is connected with a pipeline between the gas-liquid separator and the second air suction port of the second air cylinder; the second end of the second branch is connected with the inlet of the second heat exchanger; the first branch is provided with a third control valve, and the second branch is provided with a second control valve; the outlet of the first throttling element is connected with the inlet of the gas-liquid separator, the inlet of the second throttling element is connected with the bottom outlet of the gas-liquid separator, and the top outlet of the gas-liquid separator is connected with a pipeline between the first exhaust port and the second air suction port.
Further, the air conditioning system comprises a three-cylinder two-stage enthalpy-increasing operation mode, when the air conditioning system is in the three-cylinder two-stage enthalpy-increasing operation mode, the second control valve is closed, and the third control valve is opened; the first and third cylinders suck the refrigerant from the outlet of the second heat exchanger, the compressed refrigerant is discharged from the first and third exhaust ports, the refrigerant discharged from the first and third cylinders is mixed with the medium-pressure refrigerant entering the compressor from the gas-liquid separator, and the mixed refrigerant is sucked by the second cylinder; the high-temperature and high-pressure refrigerant discharged from the second cylinder is condensed into high-pressure supercooled refrigerant through the first heat exchanger, and the supercooled refrigerant is throttled into medium-pressure two-phase refrigerant through the first throttling element to enter the gas-liquid separator; in the gas-liquid separator, the refrigerant is divided into two paths, and the gaseous refrigerant is sucked by the second cylinder after being mixed with the exhaust gases of the first cylinder and the third cylinder through the gas-liquid separator; the liquid refrigerant flows out from the bottom outlet of the gas-liquid separator, is throttled into low-temperature low-pressure refrigerant by the second throttling element and enters the second heat exchanger, and is evaporated into low-pressure superheated refrigerant in the second heat exchanger to be sucked by the first air suction port and the third air suction port.
Further, the air conditioning system further comprises a two-stage enthalpy increasing unloading mode, when the air conditioning system is in the two-stage enthalpy increasing unloading operation mode, the second control valve is opened, and the third control valve is closed; the first cylinder and the third cylinder suck the refrigerant from the outlet of the second heat exchanger, compress the refrigerant and discharge the compressed refrigerant from the first exhaust port and the third exhaust port; the refrigerant discharged from the first cylinder is mixed with the medium pressure refrigerant entering the compressor from the gas-liquid separator, and the mixed refrigerant is sucked by the second cylinder together; the refrigerant discharged from the third exhaust port enters the second heat exchanger inlet through the second control valve; the high-temperature and high-pressure refrigerant discharged from the second cylinder is condensed into high-pressure supercooled refrigerant through the first heat exchanger, and the supercooled refrigerant is throttled into medium-pressure two-phase refrigerant through the first throttling element to enter the gas-liquid separator; in the gas-liquid separator, the refrigerant is divided into two paths, and the gaseous refrigerant is sucked by the second cylinder after being mixed with the exhaust gas of the first cylinder through the gas-liquid separator; the liquid refrigerant flows out from the bottom outlet of the gas-liquid separator, is throttled by the second throttling element to be mixed with the exhaust gas from the third cylinder, then enters the second heat exchanger, is evaporated into low-pressure overheated refrigerant in the second heat exchanger, and is sucked by the first air suction port and the third air suction port.
Further, the air conditioning system further comprises a two-stage unloading operation mode, when the air conditioning system is in the two-stage unloading operation mode, the second control valve is opened, and the third control valve is closed; the first cylinder and the third cylinder suck the refrigerant from the second heat exchanger, compress the refrigerant and discharge the refrigerant from the first exhaust port and the third exhaust port; the refrigerant discharged from the first cylinder is sucked by the second cylinder; the refrigerant discharged from the third exhaust port enters an inlet of the second heat exchanger through the second control valve; the high-temperature and high-pressure refrigerant discharged from the second cylinder is condensed into high-pressure supercooled refrigerant through the first heat exchanger, and the supercooled refrigerant is throttled into medium-pressure two-phase refrigerant through the first throttling element to enter the gas-liquid separator; the refrigerant in the gas-liquid separator flows out from the bottom outlet of the gas-liquid separator, is throttled by the second throttling element to be mixed with the exhaust gas from the third cylinder, then enters the second heat exchanger, is evaporated into low-pressure overheated refrigerant in the second heat exchanger, and is sucked by the first air suction port and the third air suction port.
Further, the first control valve is a stop valve or a solenoid valve.
Further, the second control valve and the third control valve are stop valves or solenoid valves.
Further, the compressor is a rotor compressor or a scroll compressor or a piston compressor.
By applying the technical scheme of the application, the compressor and the second heat exchanger are provided with the unloading channels, and the compressor is convenient to unload through the action of the unloading channels.
Drawings
The accompanying drawings, which are included to provide a further understanding of the application and are incorporated in and constitute a part of this specification, illustrate embodiments of the application and together with the description serve to explain the application. In the drawings:
Fig. 1 schematically shows a connection relationship diagram of a first embodiment of an air conditioning system of the present invention;
FIG. 2 schematically illustrates a single stage compression connection diagram of the air conditioning system of the present invention;
FIG. 3 schematically illustrates a schematic diagram of the air conditioning system of FIG. 2 in a full load mode of operation;
FIG. 4 schematically illustrates a schematic diagram of the air conditioning system of FIG. 2 in an unloaded mode of operation;
fig. 5 schematically shows a connection relationship diagram of a second embodiment of the air conditioning system of the present invention;
FIG. 6 schematically illustrates a schematic diagram of the air conditioning system of FIG. 5 in a single-stage, dual-cylinder mode of operation;
FIG. 7 schematically illustrates a schematic diagram of the air conditioning system of FIG. 5 in single cylinder operation;
fig. 8 schematically shows a connection relationship diagram of a third embodiment of the air conditioning system of the present invention;
FIG. 9 schematically illustrates a schematic diagram of the air conditioning system of FIG. 8 in an enthalpy-increasing mode of operation;
FIG. 10 schematically illustrates a schematic diagram of the air conditioning system of FIG. 8 in an unloaded mode of operation;
fig. 11 schematically shows a connection relationship diagram of a fourth embodiment of the air conditioning system of the present invention;
FIG. 12 schematically illustrates a schematic diagram of the air conditioning system of FIG. 8 in a dual stage mode of operation;
FIG. 13 schematically illustrates a schematic diagram of the air conditioning system of FIG. 8 in a single stage mode of operation;
fig. 14 schematically shows a connection relationship diagram of a fifth embodiment of the air conditioning system of the present invention;
FIG. 15 schematically illustrates a schematic diagram of the air conditioning system of FIG. 14 in a three-cylinder dual stage mode of operation;
FIG. 16 schematically illustrates a schematic diagram of the air conditioning system of FIG. 14 in a single cylinder unloaded mode of operation;
fig. 17 schematically shows a connection relationship diagram of a sixth embodiment of the air conditioning system of the present invention;
FIG. 18 schematically illustrates a schematic diagram of the air conditioning system of FIG. 14 in a three-cylinder dual stage enthalpy increasing mode of operation;
FIG. 19 schematically illustrates a schematic diagram of the air conditioning system of FIG. 18 in a dual stage enthalpy increasing unloading mode of operation;
fig. 20 schematically illustrates a schematic diagram of the air conditioning system of fig. 18 in a dual-stage unloading mode of operation.
Wherein the above figures include the following reference numerals:
1. a compressor; 11. a first cylinder; 111. a first air suction port; 112. a first exhaust port; 12. a second cylinder; 121. a second air suction port; 122. a second exhaust port; 13. a third cylinder; 131. a third air suction port; 132. a third exhaust port; 2. a first heat exchanger; 3. a second heat exchanger; 4. a first throttling element; 5. a gas-liquid separator; 6. a second throttling element; 7. a second control valve; 8. a third control valve; 9. an unloading channel; 92. a main pipe; 91. a first branch; 93. a second branch; 10. and (5) an advanced exhaust device.
Detailed Description
It should be noted that, without conflict, the embodiments of the present application and features of the embodiments may be combined with each other. The application will be described in detail below with reference to the drawings in connection with embodiments.
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 exemplary embodiments according to the present application. As used herein, the singular is also intended to include the plural unless the context clearly indicates otherwise, and furthermore, it is to be understood that the terms "comprises" and/or "comprising" when used in this specification are taken to specify the presence of stated features, steps, operations, devices, components, and/or combinations thereof.
It should be noted that the terms "first," "second," and the like in the description and the claims of the present application and the above figures are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used may be interchanged where appropriate such that embodiments of the application described herein may be capable of being practiced otherwise than as specifically illustrated and described. 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 … …," "upper surface at … …," "above," and the like, may be used herein for ease of description to describe one device or feature's spatial location relative 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 in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is turned over, elements described as "above" or "over" other devices or structures would then be oriented "below" or "beneath" the other devices or structures. Thus, the exemplary term "above … …" may include both orientations of "above … …" and "below … …". The device may also be positioned in other different ways (rotated 90 degrees or at other orientations) and the spatially relative descriptors used herein interpreted accordingly.
Referring to fig. 1, according to a first embodiment of the present invention, there is provided an air conditioning system including a compressor 1, a first heat exchanger 2, a first throttling element 4, and a second heat exchanger 3 sequentially disposed on the same circuit, and an unloading passage 9 connected between the compressor 1 and the second heat exchanger 3 to unload the compressor 1.
According to the above structure, it can be known that the unloading channels 9 are provided in the compressor 1 and the second heat exchanger 3 in this embodiment, and by the effect of the unloading channels 9, the compressor 1 is convenient to be unloaded, and compared with the structure in the prior art, the air conditioning system in this embodiment has a simple structure, and can unload the compressor 1 only by the effect of one unloading channel 9, so that the unloading problem of the compressor 1 under the partial load is effectively solved, the compressor 1 is ensured to always operate in a higher frequency range, and the motor efficiency and the volumetric efficiency of the compressor 1 under the low pressure ratio and the low frequency are further effectively improved, and the efficiency of the air conditioning system under the partial load is further improved.
Referring to fig. 2, the air conditioning system in this embodiment further includes a second throttling element 6, where the second throttling element 6 is disposed on the refrigerant pipe between the first throttling element 4 and the second heat exchanger 3, a first end of the unloading channel 9 is connected to the compressor 1, and a second end of the unloading channel 9 is connected to the refrigerant pipe between the first throttling element 4 and the second throttling element 6 or at an inlet of the second throttling element 6, so as to facilitate unloading the compressor 1.
The compressor 1 includes a first cylinder 11, on which an advance exhaust device 10 is provided, the advance exhaust device 10 being provided with an advance exhaust port (not shown in the figure) and a first control valve (not shown in the figure) for controlling the opening and closing of the advance exhaust port, and a first end of an unloading passage 9 being connected to the advance exhaust port.
As shown in fig. 3, the air conditioning system is in the full load mode of operation: when the cold and heat quantity demand is large, the air conditioning system is in a full-load operation mode, high-temperature and high-pressure refrigerant gas is discharged from a first exhaust port 112 on a first cylinder 11 on the compressor 1 and condensed into high-pressure supercooled liquid through a first heat exchanger 2, the high-pressure supercooled liquid is throttled into intermediate-pressure refrigerant through a first throttling element 4 and then into low-temperature and low-pressure refrigerant through a second throttling element 6, the low-temperature and low-pressure refrigerant enters a second heat exchanger 3, the refrigerant is evaporated in the second heat exchanger 3 and becomes gaseous refrigerant, and the gaseous refrigerant is sucked into a first air suction port 111 of the compressor 1; preferably, during the throttling process of the high-pressure supercooled refrigerant through the first throttling element 4, the first throttling element 4 can be fully opened, and the throttling process of the refrigerant from high pressure to low pressure can be fully carried out by the second throttling element 6; whether the first throttling element 4 throttles the refrigerant to medium pressure or the first throttling element 4 is fully opened, the advance exhaust 10 connected to the unloading passage 9 is always in a closed state because the pressure in the compression chamber is smaller than the back pressure of the advance exhaust 10 when the rotor of the compressor 1 rotates past the advance exhaust 10. Further, for eliminating the second throttling element 6 and setting the first control valve on the advance exhaust device 10, the high-pressure supercooled refrigerant throttles the refrigerant from high pressure to low pressure through the first throttling element 4, the first control valve on the advance exhaust device 10 is tightly closed, and after the system is balanced, the back pressure of the advance exhaust device 10 is equal to the pressure in the compression cavity corresponding to the rotor rotating through the advance exhaust device 10.
As shown in fig. 4, the air conditioning system is operated in the unloading mode of operation; when the air conditioning system operates under a medium-small load condition, the refrigerant from the first exhaust port 112 of the compressor 1 is condensed into high-pressure supercooled refrigerant through the first heat exchanger 2, the high-pressure supercooled refrigerant is throttled to low-pressure gaseous refrigerant through the first throttling element 4, the back pressure of the early exhaust device 10 is the pressure behind the first throttling element 4, at the moment, the back pressure is only different from the pressure of the first air suction port 111 of the compressor 1 by the resistance pressure drop of the pipeline and the second heat exchanger 3, the difference is small, when the pressure in the compression cavity of the compressor 1 is larger than the back pressure, the first control valve on the early exhaust device 10 is opened, the refrigerant is discharged from the compression cavity through the early exhaust device 10, the refrigerant throttled by the unloading channel 9 and the first throttling element 4 is mixed and then enters the second heat exchanger 3, and the refrigerant is sucked from the first air suction port 111 of the compressor 1 after being evaporated by the second heat exchanger 3. Further, for a system in which a valve is provided on the air-supplementing branch while the second throttling element 6 is eliminated, the air-supplementing branch valve is fully opened during unloading operation, and when the pressure in the compression chamber is greater than the back pressure of the advance exhaust device 10, the first control valve on the advance exhaust device 10 is opened and is not closed until the rotor rotates past the advance exhaust device 10.
Referring to fig. 5, according to a second embodiment of the present invention, there is provided an air conditioning system, which is basically identical in structure to the air conditioning system of the first embodiment except that the compressor 1 of the present embodiment includes a first cylinder 11 and a second cylinder 12, the first cylinder 11 includes a first suction port 111 and a first discharge port 112, the second cylinder 12 includes a second suction port 121 and a second discharge port 122, the first suction port 111 and the second suction port 121 are both connected to an outlet of the second heat exchanger 3, and the second discharge port 122 is connected to an inlet of the first heat exchanger 2 through a refrigerant pipe;
the unloading channel 9 comprises a main pipe 92, a first branch 91 and a second branch 93, wherein a first end of the main pipe 92 is connected to the second exhaust port 122 of the second cylinder 12, a second end of the main pipe 92 is connected to a first end of the first branch 91 and a first end of the second branch 93, a second end of the first branch 91 and a pipe connection between the first throttling element 4 and the second throttling element 6, and a second end of the second branch 93 is connected to the inlet of the first heat exchanger 2; the first branch 91 is provided with a second control valve 7 and the second branch 93 is provided with a third control valve 8.
Referring to fig. 6, when the air conditioning system in the present embodiment is in the double-cylinder operation mode: in this case, the second control valve 7 of the compressor 1 is closed, the third control valve 8 is opened, and the refrigerant is discharged from the second discharge port 122 and the first discharge port 112, wherein the refrigerant of the second cylinder 12 is mixed with the refrigerant of the first cylinder 11 through the third control valve 8 and then enters the first heat exchanger 2, the refrigerant is condensed into a high-pressure supercooled liquid in the first heat exchanger 2, the high-pressure refrigerant is changed into a low-temperature low-pressure refrigerant through the first throttling element 4 and enters the second heat exchanger 3, and the two-phase low-temperature refrigerant is evaporated into superheated vapor in the second heat exchanger 3 and is sucked into the first suction port 111 and the second suction port 121 of the compressor 1, thereby completing the cycle.
Referring to fig. 7, when the air conditioning system in the present embodiment is in the single-cylinder operation mode: the second control valve 7 of the compressor 1 is opened, the third control valve 8 is closed, the high-temperature and high-pressure refrigerant entering the first heat exchanger 2 is all from the first cylinder 11 of the compressor 1 due to the closing of the third control valve 8 of the compressor 1, the part of the refrigerant is condensed into high-pressure supercooled refrigerant in the first heat exchanger 2 and throttled into low-temperature and low-pressure two-phase refrigerant by the first throttling element 4, and the back pressure of the second exhaust port 122 of the second cylinder 12 of the compressor 1 is equal to the inlet pressure of the second heat exchanger 3 due to the opening of the second control valve 7, so that when the pressure in the compression cavity of the second cylinder 12 is greater than the back pressure, the refrigerant is discharged from the second exhaust port 122 and mixed with the low-temperature and low-pressure refrigerant throttled by the first throttling element 4 into the second heat exchanger 3, and the refrigerant is sucked into the first and second suction ports 111 and 121 of the compressor 1 after the second heat exchanger 3 is evaporated.
Referring to fig. 8, according to a third embodiment of the present invention, there is provided an air conditioning system which is basically identical in structure to the air conditioning system in the first embodiment except that the compressor 1 in the first embodiment includes a first cylinder 11 and a second cylinder 12, and the air conditioning system further includes a gas-liquid separator 5, wherein the first cylinder 11 is provided with an advance exhaust device 10, the first cylinder 11 includes a first suction port 111 and a first exhaust port 112, the second cylinder 12 includes a second suction port 121 and a second exhaust port 122, the first suction port 111 is connected to an outlet of the second heat exchanger 3, the second exhaust port 122 and the first exhaust port 112 are both connected to an inlet of the first heat exchanger 2, the advance exhaust device 10 includes an advance exhaust port and a first control valve for controlling opening and closing of the advance exhaust port, the advance exhaust port is connected to the second suction port 121 through a pipe, a first end of the unloading passage 9 and a pipe between the advance exhaust port and the second suction port are connected to a top outlet of the gas-liquid separator 5, an outlet of the first throttling element 4 is connected to an outlet of the gas-liquid separator 5, and an outlet of the second throttling element 4 is connected to an inlet of the gas-liquid separator 5 is connected to an outlet of the bottom of the second throttling element 6.
Referring to fig. 9, when the air conditioning system in the present embodiment is in the enthalpy-increasing operation mode: the refrigerant discharged from the first cylinder 11 and the second cylinder 12 of the compressor 1 is mixed and then enters the first heat exchanger 2, the refrigerant is condensed into high-pressure supercooled refrigerant in the first heat exchanger 2, the high-pressure supercooled refrigerant is throttled to be medium-pressure two-phase refrigerant through the first throttling element 4 and enters the gas-liquid separator 5, in the gas-liquid separator 5, the liquid refrigerant enters the second throttling element 6 through the bottom outlet of the gas-liquid separator 5 and throttled to be low-temperature low-pressure refrigerant, and then enters the second heat exchanger 3 to be evaporated to be low-pressure overheat refrigerant, and finally the first cylinder 11 of the compressor 1 is sucked; gaseous refrigerant in the gas-liquid separator 5 flows out through an outlet at the top of the gas-liquid separator, passes through a gas supplementing branch and is finally sucked in by a second air suction port 121 of a second air cylinder 12 of the compressor 1, so that the cycle is completed; it should be further noted that, in the enthalpy-increasing operation mode, the back pressure of the advance exhaust device 10 is the intermediate pressure of the gas-liquid separator 5 after being throttled by the first throttling element 4, and the advance exhaust device 10 is set at a reasonable position, so that the pressure in the compression chamber is still lower than the intermediate pressure when the first cylinder 11 of the compressor 1 rotates past the advance exhaust device 10, and the advance exhaust device 10 is always in the closed state in the enthalpy-increasing mode. Of course, in the actual design process, the air conditioning system in the present embodiment may not be provided with the advance exhaust device 10.
Referring to fig. 10, the air conditioning system in the present embodiment is in the unloading operation mode: when the system is operated in an unloading mode, the second throttling element 6 is fully opened, high-temperature and high-pressure refrigerant discharged from the first cylinder 11 and the second cylinder 12 of the compressor 1 is condensed into high-pressure supercooled liquid through the first heat exchanger 2, enters the first throttling element 4 to be throttled into low-pressure and low-temperature two-phase refrigerant, and enters the gas-liquid separator 5; because the pressure in the gas-liquid separator 5 is only slightly greater than the suction pressure of the first cylinder 11 of the compressor 1, and the back pressure of the early exhaust device 10 on the first cylinder 11 of the compressor 1 is the pressure in the gas-liquid separator 5, when the pressure in the compression cavity of the first cylinder 11 of the compressor is greater than the back pressure, the first control valve on the early exhaust device 10 is opened, the refrigerant in the first cylinder 11 of the compressor is discharged through the early exhaust device 10, the refrigerant is divided into two paths, one path enters the suction cavity of the second cylinder 12 of the compressor 1, the other path enters the second heat exchanger 3 after being mixed with the low-temperature low-pressure two-phase refrigerant throttled by the first throttling element 4 through the gas-liquid separator 5, the low-temperature two-phase refrigerant is evaporated in the second heat exchanger 3 to become low-temperature overheated refrigerant, and finally is sucked by the first cylinder 11; it should be further noted that the refrigerant exiting the advance exhaust device 10 can be split into two paths, because the displacement of the second cylinder 12 of the dual-cylinder enthalpy-increasing compressor is small, when the advance exhaust device 10 is set at a reasonable position, only a small portion of the refrigerant exiting the first cylinder 11 enters the second suction port 121, and a large portion of the refrigerant will be discharged into the gas-liquid separator 5.
Referring to fig. 11, according to a fourth embodiment of the present invention, there is provided an air conditioning system which is basically identical in structure to the air conditioning system in the first embodiment except that the compressor 1 includes a first cylinder 11 and a second cylinder 12, the air conditioning system further includes a gas-liquid separator 5, the first cylinder 11 includes a first suction port 111 and a first discharge port 112, the second cylinder 12 includes a second suction port 121 and a second discharge port 122, the first suction port 111 is connected to an outlet of the second heat exchanger 3, the first discharge port 112 is connected to the second suction port 121, the second discharge port 122 is connected to an inlet of the first heat exchanger 2, a first end of the unloading passage 9 is connected to a pipe between the first discharge port 112 and the second suction port 121, a second end of the unloading passage 9 is connected to a top outlet of the gas-liquid separator 5, an outlet of the first throttling element 4 is connected to an inlet of the gas-liquid separator 5, and an inlet of the second throttling element 6 is connected to a bottom outlet of the gas-liquid separator 5.
Referring to fig. 12, when the air conditioning system in the present embodiment is in the two-stage operation mode: the high-temperature and high-pressure refrigerant discharged from the second cylinder 12 of the compressor 1 is condensed into high-pressure supercooled liquid through the first heat exchanger 2, and the supercooled refrigerant discharged from the first heat exchanger 2 is throttled to medium-pressure two-phase refrigerant through the first throttling element 4 to enter the gas-liquid separator 5; in the gas-liquid separator 5, the refrigerant is divided into two paths, wherein the liquid refrigerant flows out from the bottom outlet of the bottom gas-liquid separator 5, becomes low-temperature low-pressure refrigerant through the second throttling element 6 and enters the second heat exchanger 3, and the refrigerant is evaporated in the second heat exchanger 3 and becomes low-pressure superheated refrigerant to be sucked by the first cylinder 11 of the compressor 1; the other path of refrigerant gas in the gas-liquid separator 5 flows out through the top outlet at the top of the gas-liquid separator 5, is mixed with the refrigerant discharged from the first cylinder 11 of the compressor 1, and is sucked into the second suction port 121 of the second cylinder 12 of the compressor 1, thereby completing the cycle.
Referring to fig. 13, when the air conditioning system in the present embodiment is in the single-stage operation mode: in the single-stage operation mode, the second throttling element 6 is fully opened, the refrigerant discharged from the second cylinder 12 of the compressor 1 is condensed into supercooled liquid through the first heat exchanger 2, throttled into low-temperature low-pressure refrigerant through the first throttling element 4 and enters the gas-liquid separator 5, the back pressure of the first exhaust port 112 of the compressor 1 is equal to the pressure inside the gas-liquid separator 5, the difference between the pressure in the gas-liquid separator 5 and the suction pressure is the pressure drop of the pipeline and the second heat exchanger 3, and the difference is small, so when the pressure in the compression cavity of the first cylinder 11 of the compressor 1 is larger than the back pressure, the refrigerant in the first cylinder 11 is discharged, the discharged refrigerant is divided into two parts, one part is sucked in by the second suction port 121 of the compressor 1, the other part is mixed with the low-temperature low-pressure two-phase refrigerant throttled through the first throttling element 4 and enters the second heat exchanger 3, the refrigerant is evaporated into low-pressure overheated refrigerant in the second heat exchanger 3, and finally sucked into the first suction port 111 of the first cylinder 11 of the compressor 1.
Referring to fig. 14, according to a fifth embodiment of the present invention, there is provided an air conditioning system which is basically identical in structure to the air conditioning system in the first embodiment except that the compressor 1 in the present embodiment includes a first cylinder 11, a second cylinder 12 and a third cylinder 13, the air conditioning system further includes a gas-liquid separator 5, the first cylinder 11 includes a first suction port 111 and a first discharge port 112, the second cylinder 12 includes a second suction port 121 and a second discharge port 122, the third cylinder 13 includes a third suction port 131 and a third discharge port 132, the first suction port 111 and the third suction port 131 are both connected to an outlet of the second heat exchanger 3, the first discharge port 112 and the third discharge port 132 are both connected to the second suction port 121, and the second discharge port 122 is connected to an inlet of the first heat exchanger 2;
The first end of the unloading channel 9 is connected to the conduit between the first exhaust port 112 and the second exhaust port 121 and the conduit between the third exhaust port 132 and the second exhaust port 121, the second end of the unloading channel 9 is connected to the top outlet of the gas-liquid separator 5, the outlet of the first throttling element 4 is connected to the inlet of the gas-liquid separator 5, and the inlet of the second throttling element 6 is connected to the bottom outlet of the gas-liquid separator 5.
Referring to fig. 15, the air conditioning system in this embodiment is in a three-cylinder two-stage operation mode: the first and third cylinders 11 and 13 of the compressor 1 suck the refrigerant from the outlet of the second heat exchanger 3, the compressed refrigerant is discharged from the first and third discharge ports 112 and 132, the refrigerant discharged from the first and third cylinders 11 and 13 of the compressor 1 is mixed with the medium pressure refrigerant introduced into the compressor 1 from the gas-liquid separator 5, and the mixed refrigerant is sucked by the second cylinder 12 of the compressor 1; the high-temperature and high-pressure refrigerant discharged from the second cylinder 12 is condensed into high-pressure supercooled refrigerant by the first heat exchanger 2, and the supercooled refrigerant is throttled into medium-pressure two-phase refrigerant by the first throttling element 4 to enter the gas-liquid separator 5; in the gas-liquid separator 5, the refrigerant is divided into two paths, and the gaseous refrigerant is mixed with the discharged refrigerant of the first cylinder 11 and the third cylinder 13 of the compressor 1 through the top outlet of the gas-liquid separator 5 and then is sucked by the second cylinder 12 of the compressor 1; the liquid refrigerant flows out from the bottom outlet of the gas-liquid separator 5, is throttled by the second throttling element 6 to a low-temperature low-pressure refrigerant, and enters the second heat exchanger 3, and the refrigerant is evaporated into a low-pressure superheated refrigerant in the second heat exchanger 3 and is sucked by the first suction port 111 of the first cylinder 11 and the second suction port 121 of the second cylinder 12 of the compressor 1.
Referring to fig. 16, the air conditioning system in the present embodiment is in the single cylinder unloading operation mode: the second throttling element 6 is fully open such that the pressure in the gas-liquid separator 5 is the inlet pressure of the second heat exchanger 3; in this way, the pressure in the gas-liquid separator 5 differs from the suction pressure of the first 11 and third 13 cylinders of the compressor 1 by the pressure drop of the duct and the second heat exchanger 3, obviously by a very small difference; the exhaust back pressure of the first cylinder 11 and the third cylinder 13 and the suction pressure of the second cylinder 12 are equal to the pressure in the gas-liquid separator 5, so that the refrigerant discharged from the first cylinder 11 and the third cylinder 13 of the compressor 1 is divided into two parts, one part is sucked by the second cylinder 12 of the compressor 1, and the other part enters the gas-liquid separator 5; based on the flow direction of the refrigerant, the whole system operation flow is as follows: the high-temperature and high-pressure refrigerant discharged from the second cylinder 12 of the compressor 1 is condensed into high-pressure supercooled liquid through the first heat exchanger 2, and the supercooled refrigerant is throttled into low-pressure and low-temperature two-phase refrigerant through the first throttling element 4 to enter the gas-liquid separator 5; in the gas-liquid separator 5, the low-temperature low-pressure refrigerant throttled from the first throttling element 4 enters the second heat exchanger 3 through the second throttling element 6, and in the second heat exchanger 3, the refrigerant evaporates into low-pressure superheated refrigerant, and is finally sucked in by the first suction port 111 of the first cylinder 11 and the third suction port 131 of the third cylinder 13 of the compressor 1, thereby completing the entire cycle.
Referring to fig. 17, according to a sixth embodiment of the present invention, there is provided an air conditioning system, which is basically identical in structure to the air conditioning system of the first embodiment except that the compressor 1 includes a first air cylinder 11, a second air cylinder 12, and a third air cylinder 13, the air conditioning system further includes a gas-liquid separator 5, the first air cylinder 11 includes a first air suction port 111 and a first air discharge port 112, the second air cylinder 12 includes a second air suction port 121 and a second air discharge port 122, the third air cylinder 13 includes a third air suction port 131 and a third air discharge port 132, the first air suction port 111 and the third air suction port 131 are both connected to an outlet of the second heat exchanger 3, the first air discharge port 112 is connected to the second air suction port 121, and the second air discharge port 122 is connected to an inlet of the first heat exchanger 2;
the unloading passage 9 includes a main pipe 92, a first branch 91, and a second branch 93, a first end of the main pipe 92 is connected to a third exhaust port 132 of the third cylinder 13, and a second end of the main pipe 92 is connected to a first end of the first branch 91 and a first end of the second branch 93; a second end of the first branch 91 is connected to a pipe connecting the gas-liquid separator 5 and the second suction port 121 of the second cylinder 12; a second end of the second branch 93 is connected to an inlet of the second heat exchanger 3; the first branch 91 is provided with a third control valve 8, and the second branch 93 is provided with a second control valve 7;
The outlet of the first throttling element 4 is connected with the inlet of the gas-liquid separator 5, the inlet of the second throttling element 6 is connected with the bottom outlet of the gas-liquid separator 5, and the top outlet of the gas-liquid separator 5 is connected with a pipeline between the first exhaust port 112 and the second air suction port 121.
Referring to fig. 18, when the air conditioning system in the present embodiment is in the three-cylinder two-stage enthalpy-increasing operation mode: the second control valve 7 is closed and the third control valve 8 is opened; the first and third cylinders 11 and 13 of the compressor 1 suck the refrigerant from the outlet of the second heat exchanger 3, the compressed refrigerant is discharged from the first and third discharge ports 112 and 132, the refrigerant discharged from the first and third cylinders 11 and 13 of the compressor 1 is mixed with the medium pressure refrigerant entering the compressor 1 from the gas-liquid separator 5, and the mixed refrigerant is sucked by the compressor second cylinder 12; the high-temperature and high-pressure refrigerant discharged from the second cylinder 12 is condensed into high-pressure supercooled refrigerant by the first heat exchanger 2, and the supercooled refrigerant is throttled into medium-pressure two-phase refrigerant by the first throttling element 4 to enter the gas-liquid separator 5; in the gas-liquid separator 5, the refrigerant is divided into two paths, and the gaseous refrigerant is mixed with the exhaust gas of the first cylinder 11 and the third cylinder 13 of the compressor 1 through the gas-liquid separator 5 and then is sucked by the second cylinder 12 of the compressor 1; the liquid refrigerant flows out from the bottom outlet of the gas-liquid separator 5, throttled by the second throttling element 6 to a low temperature and low pressure refrigerant, enters the second heat exchanger 3, and the refrigerant is evaporated into a low pressure superheated refrigerant in the second heat exchanger 3 and is sucked by the first suction port 111 of the first cylinder 11 and the third suction port 131 of the third cylinder 13 of the compressor 1.
Referring to fig. 19, the air conditioning system in this embodiment is in a two-stage enthalpy-increasing unloading operation mode: the second control valve 7 is opened and the third control valve 8 is closed; the first cylinder 11 and the third cylinder 13 of the compressor 1 suck the refrigerant from the outlet of the second heat exchanger 3, compress the refrigerant, and discharge the compressed refrigerant from the first discharge port 112 and the third discharge port 132; the refrigerant discharged from the first cylinder 11 of the compressor 1 is mixed with the medium pressure refrigerant introduced into the compressor 1 from the gas-liquid separator 5, and the mixed refrigerant is sucked into the second cylinder 12 of the compressor 1 together; the refrigerant discharged from the third discharge port 132 of the compressor 1 enters the inlet of the second heat exchanger 3 through the second control valve 7; the high-temperature and high-pressure refrigerant discharged from the second cylinder 12 is condensed into high-pressure supercooled refrigerant by the first heat exchanger 2, and the supercooled refrigerant is throttled into medium-pressure two-phase refrigerant by the first throttling element 4 to enter the gas-liquid separator 5; in the gas-liquid separator 5, the refrigerant is divided into two paths, and the gaseous refrigerant is mixed with the exhaust gas of the first cylinder 11 of the compressor 1 through the gas-liquid separator 5 and then is sucked by the second cylinder 12 of the compressor 1; the liquid refrigerant flows out from the bottom outlet of the gas-liquid separator 5, is throttled by the second throttling element 6 to mix the low-temperature low-pressure refrigerant with the exhaust gas from the third cylinder 13 of the compressor 1, and then enters the second heat exchanger 3, and the refrigerant is evaporated into low-pressure superheated refrigerant in the second heat exchanger 3 to be sucked by the first suction port 111 of the first cylinder 11 and the third suction port 131 of the third cylinder 13 of the compressor 1.
Referring to fig. 20, when the air conditioning system in the present embodiment is in the two-stage unloading operation mode: in this case, the second control valve 7 is opened and the third control valve 8 is closed: the first cylinder 11 and the third cylinder 13 of the compressor 1 suck the refrigerant from the outlet of the second heat exchanger 3, compress the refrigerant, and discharge the compressed refrigerant from the first discharge port 112 and the third discharge port 132; the refrigerant discharged from the first cylinder 11 of the compressor 1 is sucked by the second cylinder 12 of the compressor 1; the refrigerant discharged from the third discharge port 132 of the compressor 1 enters the inlet of the second heat exchanger 3 through the second control valve 7; the high-temperature and high-pressure refrigerant discharged from the second cylinder 12 is condensed into high-pressure supercooled refrigerant by the first heat exchanger 2, and the supercooled refrigerant is throttled into medium-pressure two-phase refrigerant by the first throttling element 4 to enter the gas-liquid separator 5; the refrigerant in the gas-liquid separator 5 flows out from the bottom outlet of the gas-liquid separator 5, is throttled by the second throttling element 6 to a low-temperature low-pressure refrigerant, is mixed with the exhaust gas from the second cylinder 12 of the compressor 1, and then enters the second heat exchanger 3, and the refrigerant is evaporated into a low-pressure superheated refrigerant in the second heat exchanger 3, which is sucked in by the first suction port 111 of the first cylinder 11 and the third suction port 131 of the third cylinder 13 of the compressor 1.
In the above embodiment, the first control valve, the second control valve 7, and the third control valve 8 are each provided as a shut-off valve or as a solenoid valve. The compressor 1 is a rotor compressor, a scroll compressor, or a piston compressor, and any other modification forms under the concept of the present invention are within the scope of the present invention.
Preferably, in the above embodiment, the first throttling element 4 and the second throttling element 6 may be configured as structural elements such as a throttle valve or a capillary tube, and any other modifications within the scope of the present invention are within the scope of the present invention.
From the above description, it can be seen that the above embodiments of the present invention achieve the following technical effects:
the invention effectively solves the unloading problem of the compressor under the partial load, so as to ensure that the compressor always operates in a higher frequency range, and further effectively improves the motor efficiency and the volumetric efficiency of the compressor under the partial load. Meanwhile, the refrigerant is discharged to the inlet of the second heat exchanger to form refrigerant recirculation, so that the dryness of the refrigerant at the inlet of the evaporator can be improved, and the flow rate of the refrigerant in the evaporator can be improved at the same time, thereby greatly improving the heat transfer coefficient of the refrigerant side. Therefore, the invention can solve the low-frequency operation problem and unloading problem of the compressor under partial load of the existing air-conditioning heat pump system, and simultaneously can effectively improve the heat exchange performance of the evaporator under medium and small load, and combines the advantages of the two layers, and the system provided by the invention can greatly improve the system performance of the existing air-conditioning heat pump under medium and small load working conditions.
The above description is only of the preferred embodiments of the present invention and is not intended to limit the present invention, but various modifications and variations can be made to the present invention by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (22)

1. An air conditioning system, characterized by comprising a compressor (1), a first heat exchanger (2), a first throttling element (4) and a second heat exchanger (3) which are arranged on the same circuit in sequence, and an unloading channel (9), wherein the unloading channel (9) is connected between the compressor (1) and the second heat exchanger (3) so as to unload the compressor (1);
the air conditioning system further comprises a second throttling element (6), wherein the second throttling element (6) is arranged on a refrigerant pipe between the first throttling element (4) and the second heat exchanger (3), a first end of the unloading channel (9) is connected with the compressor (1), and a second end of the unloading channel (9) is connected on the refrigerant pipe between the first throttling element (4) and the second throttling element (6) or at an inlet of the second throttling element (6);
The compressor (1) comprises a first air cylinder (11) and a second air cylinder (12), the first air cylinder (11) comprises a first air suction port (111) and a first air exhaust port (112), the second air cylinder (12) comprises a second air suction port (121) and a second air exhaust port (122), the first air suction port (111) and the second air suction port (121) are both connected with an outlet of the second heat exchanger (3), and the second air exhaust port (122) is connected with an inlet of the first heat exchanger (2) through a refrigerant pipe;
the unloading channel (9) comprises a main pipe (92), a first branch (91) and a second branch (93), wherein a first end of the main pipe (92) is connected with the second exhaust port (122) of the second cylinder (12), a second end of the main pipe (92) is connected with a first end of the first branch (91) and a first end of the second branch (93), a second end of the first branch (91) and a pipe between the first throttling element (4) and the second throttling element (6) are connected, and a second end of the second branch (93) is connected with an inlet of the first heat exchanger (2); the first branch (91) is provided with a second control valve (7), and the second branch (93) is provided with a third control valve (8).
2. An air conditioning system according to claim 1, characterized in that the compressor (1) comprises a first cylinder (11), an advance exhaust device (10) is arranged on the first cylinder (11), the advance exhaust device (10) is provided with an advance exhaust port and a first control valve for controlling the opening and closing of the advance exhaust port, and the first end of the unloading channel (9) is connected with the advance exhaust port.
3. An air conditioning system according to claim 2, wherein the air conditioning system comprises a full load mode of operation,
when the air conditioning system is in a full-load operation mode, high-temperature and high-pressure refrigerant gas is discharged from a first exhaust port (112) on the first air cylinder (11) and condensed into high-pressure supercooled liquid through the first heat exchanger (2), the high-pressure supercooled liquid is throttled into intermediate-pressure refrigerant through the first throttling element (4) and then into low-temperature and low-pressure refrigerant through the second throttling element (6) to enter the second heat exchanger (3), and the refrigerant is evaporated into gaseous refrigerant in the second heat exchanger (3) and is sucked into a first air suction port (111) of the compressor (1); in the full-load operating mode, the early exhaust device (10) is always in the closed state.
4. An air conditioning system according to claim 2, characterized in that the air conditioning system further comprises an unloading mode of operation, when the air conditioning system is in the unloading mode of operation, refrigerant coming out of the first discharge port (112) of the compressor (1) condenses into high-pressure supercooled refrigerant via the first heat exchanger (2), the high-pressure supercooled refrigerant throttles to low-pressure gaseous refrigerant via the first throttling element (4), the first control valve on the advance exhaust means (10) opens, refrigerant is discharged from the compression chamber via the advance exhaust means (10), mixed with the throttled refrigerant via the unloading channel (9) with the first throttling element (4) before entering the second heat exchanger (3), and refrigerant is sucked in from the first suction port (111) of the compressor (1) after evaporation in the second heat exchanger (3).
5. The air conditioning system of claim 1, wherein the air conditioning system comprises a two-tub mode of operation,
when the air conditioning system is in a double-cylinder operation mode, the second control valve (7) of the compressor (1) is closed, the third control valve (8) is opened, the refrigerant is discharged from the second exhaust port (122) and the first exhaust port (112), the refrigerant of the second air cylinder (12) is mixed with the refrigerant of the first air cylinder (11) through the third control valve (8) and then enters the first heat exchanger (2), the refrigerant is condensed into high-pressure supercooled liquid in the first heat exchanger (2), the high-pressure refrigerant becomes low-temperature low-pressure refrigerant through the first throttling element (4) and enters the second heat exchanger (3), and the two-phase low-temperature refrigerant is evaporated into superheated steam in the second heat exchanger (3) and is sucked by the first air suction port (111) and the second air suction port (121).
6. The air conditioning system according to claim 1, characterized in that the air conditioning system further comprises a single cylinder operation mode, when the air conditioning system is in the single cylinder operation mode, the second control valve (7) of the compressor (1) is opened, the third control valve (8) is closed, the high-temperature and high-pressure refrigerant entering the first heat exchanger (2) comes all from the first cylinder (11), the refrigerant is condensed into high-pressure supercooled refrigerant in the first heat exchanger (2) to be throttled into low-temperature and low-pressure two-phase refrigerant through the first throttling element (4), the refrigerant is discharged from the second exhaust port (122) to be mixed with the low-temperature and low-pressure refrigerant throttled through the first throttling element (4) into the second heat exchanger (3) when the pressure in the compression chamber of the second cylinder (12) is larger than the back pressure, and the refrigerant is sucked into the second heat exchanger (3) through the first suction port (111) and the second suction port (121) after being evaporated in the second heat exchanger (3).
7. An air conditioning system according to claim 1, characterized in that the compressor (1) comprises a first cylinder (11) and a second cylinder (12), in that the air conditioning system is further provided with a gas-liquid separator (5), wherein the first cylinder (11) is provided with a lead-in exhaust (10), the first cylinder (11) comprises a first suction port (111) and a first exhaust port (112), the second cylinder (12) comprises a second suction port (121) and a second exhaust port (122), the first suction port (111) is connected with the outlet of the second heat exchanger (3), the second exhaust port (122) and the first exhaust port (112) are both connected with the inlet of the first heat exchanger (2), the lead-in exhaust (10) comprises a lead-in exhaust and a first control valve for controlling the opening and closing of the lead-in exhaust, the lead-in exhaust port is connected with the second suction port (121) by a pipe, the first end of the unloading channel (9) and the exhaust port are connected with the outlet of the second pipe (121), the first end of the unloading channel (9) is connected with the inlet of the second pipe (121), the top part (5) is connected with the inlet of the top part of the separator (4), the inlet of the second throttling element (6) is connected with the bottom outlet of the gas-liquid separator (5).
8. An air conditioning system according to claim 7, characterized in that the air conditioning system comprises an enthalpy-increasing operation mode, when the air conditioning system is in the enthalpy-increasing operation mode, the refrigerant discharged from the first cylinder (11) and the second cylinder (12) of the compressor (1) is mixed and then enters the first heat exchanger (2), the refrigerant is condensed into high-pressure supercooled refrigerant in the first heat exchanger (2), the high-pressure supercooled refrigerant is throttled into medium-pressure two-phase refrigerant by the first throttling element (4) and enters a gas-liquid separator (5), in the gas-liquid separator (5), the liquid refrigerant enters the second throttling element (6) through a bottom outlet of the gas-liquid separator (5) and then enters the second heat exchanger (3) to be evaporated into low-pressure supercooled refrigerant, and finally is sucked into the first cylinder (11) of the compressor (1); gaseous refrigerant in the gas-liquid separator (5) flows out through a top outlet at the top of the gas-liquid separator (5) and is sucked by the second air suction port (121), and in the enthalpy increasing operation mode, the advance air discharge port is always in a closed state.
9. The air conditioning system according to claim 7, characterized in that the air conditioning system further comprises an unloading mode of operation, when the air conditioning system is in the unloading mode of operation, the second throttling element (6) is fully open, high temperature and high pressure refrigerant discharged from the first cylinder (11) and the second cylinder (12) is condensed into high pressure supercooled liquid by the first heat exchanger (2) to enter the first throttling element (4) to be throttled into low pressure and low temperature two-phase refrigerant to enter the gas-liquid separator (5); when the pressure in a compression cavity of a first cylinder (11) of the compressor is larger than the pressure in the gas-liquid separator (5), a first control valve of an advanced exhaust device (10) arranged on the first cylinder (11) is opened, the refrigerant in the first cylinder (11) is discharged through an advanced exhaust port, the discharged refrigerant is divided into two paths, one path enters the second cylinder (12), the other path enters the second heat exchanger (3) after being mixed with the low-temperature low-pressure two-phase refrigerant throttled by the first throttling element (4) through the gas-liquid separator (5), the low-temperature two-phase refrigerant is evaporated into low-temperature overheated refrigerant in the second heat exchanger (3), and finally is sucked by the first air suction port (111).
10. Air conditioning system according to claim 1, characterized in that the compressor (1) comprises a first air cylinder (11) and a second air cylinder (12), that a gas-liquid separator (5) is further provided in the air conditioning system, that the first air cylinder (11) comprises a first air suction opening (111) and a first air discharge opening (112), that the second air cylinder (12) comprises a second air suction opening (121) and a second air discharge opening (122), that the first air suction opening (111) is connected to the outlet of the second heat exchanger (3), that the first air discharge opening (112) is connected to the second air suction opening (121), that the second air discharge opening (122) is connected to the inlet of the first heat exchanger (2), that a first end of the unloading channel (9) is connected to a pipe between the first air discharge opening (112) and the second air suction opening (121), that a second end of the unloading channel (9) is connected to the top outlet of the gas-liquid separator (5), that an outlet of the first throttling element (4) is connected to the inlet of the gas-liquid separator (5), and that the outlet of the unloading channel (9) is connected to the bottom of the gas-liquid separator (6).
11. The air conditioning system according to claim 10, characterized in that it comprises a two-stage operation mode, when the air conditioning system is in which high-temperature and high-pressure refrigerant discharged from the second cylinder (12) of the compressor (1) is condensed into high-pressure supercooled liquid by the first heat exchanger (2), the supercooled refrigerant exiting the first heat exchanger (2) being throttled by the first throttling element (4) to medium-pressure two-phase refrigerant entering the gas-liquid separator (5); in the gas-liquid separator (5), the refrigerant is divided into two paths, wherein the liquid refrigerant flows out from the bottom outlet of the gas-liquid separator (5) and is changed into low-temperature low-pressure refrigerant through the second throttling element (6) to enter the second heat exchanger (3),
The refrigerant is evaporated in the second heat exchanger (3) to become low-pressure superheated refrigerant which is sucked by the first cylinder (11); the other path of refrigerant gas in the gas-liquid separator (5) flows out from the top outlet at the top of the gas-liquid separator (5), is mixed with the refrigerant discharged by the first air cylinder (11) and is sucked by the second air suction port (121), so that the cycle is completed.
12. An air conditioning system according to claim 10, characterized in that the air conditioning system further comprises a single-stage operation mode, when the air conditioning system is in the single-stage operation mode, the second throttling element (6) is fully opened, the refrigerant discharged from the second air cylinder (12) is condensed into supercooled liquid through the first heat exchanger (2), the low-temperature low-pressure refrigerant is throttled through the first throttling element (4) to enter the air-liquid separator (5), when the pressure in the compression cavity of the first air cylinder (11) is greater than the pressure of the air-liquid separator (5), the refrigerant in the first air cylinder (11) is discharged, the discharged refrigerant is divided into two parts, one part is sucked in through the second air suction port (121), the other part is mixed with the low-temperature low-pressure two-phase refrigerant throttled through the first throttling element (4) to enter the second heat exchanger (3), the refrigerant is evaporated in the second heat exchanger (3) to be finally overheated by the first air suction port (111).
13. An air conditioning system according to claim 1, characterized in that the compressor (1) comprises a first cylinder (11), a second cylinder (12) and a third cylinder (13), the air conditioning system further comprising a gas-liquid separator (5), the first cylinder (11) comprising a first suction port (111) and a first discharge port (112), the second cylinder (12) comprising a second suction port (121) and a second discharge port (122), the third cylinder (13) comprising a third suction port (131) and a third discharge port (132), the first suction port (111) and the third suction port (131) being both connected to the outlet of the second heat exchanger (3), the first discharge port (112) and the third discharge port (132) being both connected to the second suction port (121), the second discharge port (122) being connected to the inlet of the first heat exchanger (2);
the first end of the unloading channel (9) is connected with a pipeline between the first air outlet (112) and the second air inlet (121) and a pipeline between the third air outlet (132) and the second air inlet (121), the second end of the unloading channel (9) is connected with the top outlet of the gas-liquid separator (5), the outlet of the first throttling element (4) is connected with the inlet of the gas-liquid separator (5), and the inlet of the second throttling element (6) is connected with the bottom outlet of the gas-liquid separator (5).
14. The air conditioning system according to claim 13, characterized in that the air conditioning system comprises a three-cylinder two-stage operation mode, when the air conditioning system is in the three-cylinder two-stage operation mode, the first cylinder (11) and the third cylinder (13) suck in refrigerant from the outlet of the second heat exchanger (3), after compression, the refrigerant discharged from the first exhaust port (112) and the third exhaust port (132), the refrigerant discharged from the first cylinder (11) and the third cylinder (13) is mixed with medium-pressure refrigerant entering the compressor (1) from the gas-liquid separator (5), and the mixed refrigerant is sucked together by the second cylinder (12); high-temperature and high-pressure refrigerant discharged from the second cylinder (12) is condensed into high-pressure supercooled refrigerant through the first heat exchanger (2), and the supercooled refrigerant is throttled into medium-pressure two-phase refrigerant through the first throttling element (4) to enter the gas-liquid separator (5); in the gas-liquid separator (5), the refrigerant is divided into two paths, and the gaseous refrigerant is sucked by the second cylinder (12) after being mixed with the refrigerant discharged by the first cylinder (11) and the third cylinder (13) through the top outlet of the gas-liquid separator (5); the liquid refrigerant flows out from the bottom outlet of the gas-liquid separator (5), is throttled by the second throttling element (6) to be low-temperature low-pressure refrigerant and enters the second heat exchanger (3), and the refrigerant is evaporated into low-pressure superheated refrigerant in the second heat exchanger (3) and is sucked by the first air suction port (111) and the third air suction port (131).
15. An air conditioning system according to claim 14, characterized in that the air conditioning system further comprises a single cylinder unloading mode of operation, when the air conditioning system is in the single cylinder unloading mode of operation, the second throttling element (6) is fully open, the refrigerant discharged from the first cylinder (11) and the third cylinder (13) being divided into two parts, one part being sucked by the second cylinder (12) and the other part entering the gas-liquid separator (5); high-temperature and high-pressure refrigerant discharged from the second cylinder (12) is condensed into high-pressure supercooled liquid through the first heat exchanger (2), and the supercooled refrigerant is throttled into low-pressure and low-temperature two-phase refrigerant through the first throttling element (4) to enter the gas-liquid separator (5); in the gas-liquid separator (5), low-temperature low-pressure refrigerant throttled from the first throttling element (4) enters the second heat exchanger (3) through the second throttling element (6), and in the second heat exchanger (3), the refrigerant evaporates into low-pressure superheated refrigerant, and is finally sucked in by the first suction port (111) and the third suction port (131).
16. An air conditioning system according to claim 1, characterized in that the compressor (1) comprises a first cylinder (11), a second cylinder (12) and a third cylinder (13), the air conditioning system further comprising a gas-liquid separator (5), the first cylinder (11) comprising a first suction port (111) and a first discharge port (112), the second cylinder (12) comprising a second suction port (121) and a second discharge port (122), the third cylinder (13) comprising a third suction port (131) and a third discharge port (132), the first suction port (111) and the third suction port (131) being both connected to the outlet of the second heat exchanger (3), the first discharge port (112) and the third discharge port (132) being connected to the second suction port (121), the second discharge port (122) being connected to the inlet of the first heat exchanger (2);
The unloading channel (9) comprises a main pipeline (92), a first branch (91) and a second branch (93), wherein the first end of the main pipeline (92) is connected with the third exhaust port (132) of the third cylinder (13), and the second end of the main pipeline (92) is connected with the first end of the first branch (91) and the first end of the second branch (93); the second end of the first branch (91) is connected with a pipeline between the gas-liquid separator (5) and a second air suction port (121) of the second air cylinder (12); the second end of the second branch (93) is connected with the inlet of the second heat exchanger (3); a third control valve (8) is arranged on the first branch (91), and a second control valve (7) is arranged on the second branch (93);
the outlet of the first throttling element (4) is connected with the inlet of the gas-liquid separator (5), the inlet of the second throttling element (6) is connected with the bottom outlet of the gas-liquid separator (5), and the top outlet of the gas-liquid separator (5) is connected with a pipeline between the first exhaust port (112) and the second air suction port (121).
17. Air conditioning system according to claim 16, characterized in that it comprises a three-cylinder two-stage enthalpy-increasing operation mode, when the air conditioning system is in which the second control valve (7) is closed and the third control valve (8) is open; the first air cylinder (11) and the third air cylinder (13) suck the refrigerant from the outlet of the second heat exchanger (3), the refrigerant is discharged from the first exhaust port (112) and the third exhaust port (132) after being compressed, the refrigerant discharged from the first air cylinder (11) and the third air cylinder (13) is mixed with the medium-pressure refrigerant entering the compressor (1) from the gas-liquid separator (5), and the mixed refrigerant is sucked by the second air cylinder (12); high-temperature and high-pressure refrigerant discharged from the second cylinder (12) is condensed into high-pressure supercooled refrigerant through the first heat exchanger (2), and the supercooled refrigerant is throttled into medium-pressure two-phase refrigerant through the first throttling element (4) to enter the gas-liquid separator (5); in the gas-liquid separator (5), the refrigerant is divided into two paths, and the gaseous refrigerant is sucked by the second cylinder (12) after being mixed with the exhaust gases of the first cylinder (11) and the third cylinder (13) through the gas-liquid separator (5); the liquid refrigerant flows out from the bottom outlet of the gas-liquid separator (5), is throttled by the second throttling element (6) to be low-temperature low-pressure refrigerant and enters the second heat exchanger (3), and the refrigerant is evaporated into low-pressure superheated refrigerant in the second heat exchanger (3) and is sucked by the first air suction port (111) and the third air suction port (131).
18. The air conditioning system according to claim 16, characterized in that it further comprises a two-stage enthalpy-increasing unloading mode, when the air conditioning system is in a two-stage enthalpy-increasing unloading operating mode, the second control valve (7) is open and the third control valve (8) is closed; the first cylinder (11) and the third cylinder (13) suck the refrigerant from the outlet of the second heat exchanger (3), and the refrigerant is discharged from the first exhaust port (112) and the third exhaust port (132) after being compressed; the refrigerant discharged from the first cylinder (11) is mixed with the medium-pressure refrigerant entering the compressor (1) from the gas-liquid separator (5), and the mixed refrigerant is sucked by the second cylinder (12) together; refrigerant discharged from the third exhaust port (132) enters an inlet of the second heat exchanger (3) through the second control valve (7); high-temperature and high-pressure refrigerant discharged from the second cylinder (12) is condensed into high-pressure supercooled refrigerant through the first heat exchanger (2), and the supercooled refrigerant is throttled into medium-pressure two-phase refrigerant through the first throttling element (4) to enter the gas-liquid separator (5); in the gas-liquid separator (5), the refrigerant is divided into two paths, and the gaseous refrigerant is sucked by the second cylinder (12) after being mixed with the exhaust gas of the first cylinder (11) through the gas-liquid separator (5); the liquid refrigerant flows out from the bottom outlet of the gas-liquid separator (5), is throttled by the second throttling element (6) to be mixed with the exhaust gas from the third cylinder (13) and then enters the second heat exchanger (3), and the refrigerant is evaporated into low-pressure superheated refrigerant in the second heat exchanger (3) to be sucked by the first air suction port (111) and the third air suction port (131).
19. The air conditioning system according to claim 16, characterized in that it further comprises a two-stage unloading operating mode, when the air conditioning system is in which the second control valve (7) is open and the third control valve (8) is closed; the first cylinder (11) and the third cylinder (13) suck the refrigerant from the second heat exchanger (3), and discharge the refrigerant from the first exhaust port (112) and the third exhaust port (132) after compression; the refrigerant discharged from the first cylinder (11) is sucked by the second cylinder (12); refrigerant discharged from the third discharge port (132) enters an inlet of the second heat exchanger (3) through the second control valve (7); high-temperature and high-pressure refrigerant discharged from the second cylinder (12) is condensed into high-pressure supercooled refrigerant through the first heat exchanger (2), and the supercooled refrigerant is throttled into medium-pressure two-phase refrigerant through the first throttling element (4) to enter the gas-liquid separator (5); the refrigerant in the gas-liquid separator (5) flows out from the bottom outlet of the gas-liquid separator (5), is throttled by the second throttling element (6) to be mixed with the exhaust gas from the third cylinder (13) and then enters the second heat exchanger (3), and the refrigerant is evaporated into low-pressure superheated refrigerant in the second heat exchanger (3) to be sucked by the first air suction port (111) and the third air suction port (131).
20. The air conditioning system of claim 2, wherein the first control valve is a shut-off valve or a solenoid valve.
21. An air conditioning system according to claim 1, characterized in that the second control valve (7) and the third control valve (8) are shut-off valves or solenoid valves.
22. An air conditioning system according to any of claims 1 to 21, characterized in that the compressor (1) is a rotor compressor or a scroll compressor or a piston compressor.
CN201810615167.7A 2018-06-14 2018-06-14 Air Conditioning System Active CN108444155B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201810615167.7A CN108444155B (en) 2018-06-14 2018-06-14 Air Conditioning System

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201810615167.7A CN108444155B (en) 2018-06-14 2018-06-14 Air Conditioning System

Publications (2)

Publication Number Publication Date
CN108444155A CN108444155A (en) 2018-08-24
CN108444155B true CN108444155B (en) 2023-10-27

Family

ID=63207038

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201810615167.7A Active CN108444155B (en) 2018-06-14 2018-06-14 Air Conditioning System

Country Status (1)

Country Link
CN (1) CN108444155B (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112013496B (en) * 2020-09-27 2024-06-14 珠海格力电器股份有限公司 Refrigerant circulation system, control method thereof and refrigeration equipment

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2926935Y (en) * 2006-06-14 2007-07-25 珠海格力电器股份有限公司 Low-tmperature hot-pump air-conditioner system
JP2012255370A (en) * 2011-06-08 2012-12-27 Toshiba Carrier Corp Rotary compressor, and refrigeration cycle apparatus
CN204877945U (en) * 2015-08-18 2015-12-16 珠海凌达压缩机有限公司 Rolling rotor compressor
CN208332771U (en) * 2018-06-14 2019-01-04 珠海格力电器股份有限公司 Air-conditioning system

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100281894A1 (en) * 2008-01-17 2010-11-11 Carrier Corporation Capacity modulation of refrigerant vapor compression system
US20130025304A1 (en) * 2011-07-27 2013-01-31 Dorman Dennis R Loading and unloading of compressors in a cooling system

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2926935Y (en) * 2006-06-14 2007-07-25 珠海格力电器股份有限公司 Low-tmperature hot-pump air-conditioner system
JP2012255370A (en) * 2011-06-08 2012-12-27 Toshiba Carrier Corp Rotary compressor, and refrigeration cycle apparatus
CN204877945U (en) * 2015-08-18 2015-12-16 珠海凌达压缩机有限公司 Rolling rotor compressor
CN208332771U (en) * 2018-06-14 2019-01-04 珠海格力电器股份有限公司 Air-conditioning system

Also Published As

Publication number Publication date
CN108444155A (en) 2018-08-24

Similar Documents

Publication Publication Date Title
CN107576085B (en) Refrigerating system
CN110332635B (en) Double-stage compression multi-air-supplementing refrigeration heat pump system, control method and air conditioner
CN106595105B (en) Air regulator
CN107576090B (en) Refrigerating system
CN110374876A (en) Dual temperature independent compressor and air-conditioning system parallel
US11713888B2 (en) Compressor and air conditioner system
KR20190002715A (en) Pump module and compressor having same
CN107560210B (en) Refrigerating system
US11519640B2 (en) Air conditioner
CN104879942B (en) The cooling and warming circulatory system
CN108692478B (en) The control method of air-conditioning system and air-conditioning system
US20130055754A1 (en) Air conditioner
CN210569333U (en) Air conditioning system
CN108444155B (en) Air Conditioning System
CN110631286B (en) Heat exchange system and control method
CN208595732U (en) A kind of heat pump circulating system of compound defrosting
CN111059732A (en) Air conditioner and control method thereof
CN215930176U (en) Refrigerating system
CN111486609B (en) Air conditioning system and control method
CN205448417U (en) Heat exchange system
CN114838535A (en) Air conditioning system with bypass heating gas-liquid separator and heating method thereof
CN208332771U (en) Air-conditioning system
CN112178969A (en) Multi-split system and control method thereof
CN105928244A (en) Air conditioner refrigerant circulating system, air conditioner and air conditioner control method
CN109682105A (en) Air-conditioning system

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant