WO2019100913A1 - Compressor, and air conditioning system having same - Google Patents

Abstract

A compressor (1), and an air conditioning system having the same. The compressor (1) has a first pneumatic cylinder (3) and a second pneumatic cylinder (4). The first pneumatic cylinder (3) is constructed such that compression involves the entire volume of the pneumatic cylinder when a sliding vane cavity (3c) is in communication with a high-pressure refrigerant, and compression does not involve the entire volume of the pneumatic cylinder when the sliding vane cavity (3c) is in communication with a low-pressure refrigerant. The second pneumatic cylinder (4) is constructed such that compression involves the entire volume when a piston cavity (4c) is in communication with the high-pressure refrigerant, and compression involves only a portion of the volume when the piston cavity (4c) is in communication with the low-pressure refrigerant. The air conditioning system comprises the compressor (1), an outdoor heat exchanger (9), an indoor heat exchanger (14), a flash evaporator (12), a reversing valve assembly, etc. The reversing valve assembly comprises a first four-way valve (5), a second four-way valve (6), and a third four-way valve (8).

Description

Compressor and air conditioning system therewith

Cross-reference to related applications

This application claims the Chinese patent application number "201711195600.8", which was submitted by the Anhui Meizhi Precision Manufacturing Co., Ltd. on November 24, 2017, and whose invention name is "compressor and air conditioning system having the same" and the invention name is "compressor and has The priority of the Chinese Patent Application No. "201721602089.4", the entire disclosure of which is incorporated herein by reference.

Technical field

The present disclosure relates to the field of compressor technology, and in particular to a compressor and an air conditioning system therewith.

Background technique

In the related art, a variable displacement compressor is a compressor having two or more compression chambers, typically a rotary compressor having two cylinders. When the refrigeration load is large, the compressor operates at full capacity (two cylinders work simultaneously); when the refrigeration load is small, the compressor operates at partial capacity (only one of the cylinders is working and the other is not working). The air-conditioning system with variable-capacity compressor can avoid the frequent start-stop and partial load efficiency of the compressor in the fixed-speed air-conditioning system during partial load, and its SEER (cooling season energy efficiency ratio) is much higher than that of the fixed-speed air-conditioning system. Although it is still lower than the inverter air conditioner system, its cost is much lower than that of the inverter air conditioner system. It can be said that the variable capacity compressor is a compromise solution that takes into account the low cost of the fixed speed compressor and the high efficiency of the inverter compressor, and is an important direction for the development of compressor technology in recent years.

A stand-alone compression compressor is also a compressor having two or more compression chambers, typically a rotary compressor having two cylinders. One of the compression chambers compresses the low pressure gas at the outlet of the evaporator, and the other compression chamber compresses the medium pressure gas after the primary throttle is separated by the flasher or the economizer is evaporated. The independent compression cycle can reduce the throttling loss, reduce the dryness of the refrigerant entering the evaporator, and improve the heat exchange efficiency of the evaporator, thereby improving the capacity and energy efficiency of the air conditioning system under certain working conditions.

Existing compressors are usually simply one of independent compression compressors and variable displacement compressors, and cannot take into account the advantages of both compression technologies, and thus can be further improved.

Summary of the invention

The present disclosure is intended to address at least one of the technical problems existing in the prior art. To this end, the present disclosure proposes a compressor that can improve the cooling or heating efficiency under specific working conditions, and can also take into account part of the load during the transition season, thereby improving the seasonal energy efficiency.

The present disclosure has been made by the applicant based on the following recognition:

The two-cylinder variable-capacity compressor and the two-cylinder independent compression compressor are both different and related. The common feature of a two-cylinder variable-capacity compressor and a two-cylinder independent compression compressor is that the exhaust gases of both cylinders are mixed in the compressor casing and then discharged together with the exhaust port of the compressor. The difference is that when the two-cylinder variable-capacity compressor is in operation, the intake ports of the two cylinders are in the same state, the boost ratios of the two cylinders are the same, and the two cylinders are equivalent to parallel operation; and the two-cylinder independent compression compressor In operation, the first cylinder draws in from the low pressure, the second cylinder inhales from an intermediate pressure, and the boost ratios of the two cylinders are different. Both the two-cylinder variable-capacity compressor and the two-cylinder independent compression compressor have advantages and disadvantages. Therefore, there is an urgent need to provide a compressor that can operate in an independent compression mode and in a variable capacity mode, which can improve the cooling (heating) capacity or energy efficiency in a fixed working condition, and can also achieve seasonal energy efficiency. In order to take full advantage of the advantages of the two compressor technologies.

A compressor according to an embodiment of the first aspect of the present disclosure includes: a housing having an exhaust port; a compression member including a first cylinder, a second cylinder, a first slider, and a second slider a first piston, a second piston, the first cylinder has a first air inlet, a first air outlet, and a sliding slot, the first sliding piece is located in the sliding slot and the sliding slot a portion of the back of the first slider formed as a vane cavity, the first vane being configured to be pressed against the first piston when the vane cavity is pressurized with high pressure refrigerant, and The sliding vane chamber is disengaged from the first piston when passing through the low pressure refrigerant, and the second cylinder has a second suction port, a second exhaust port, a plunger chamber and a bypass hole, and the plunger chamber is disposed a plunger is disposed in the plunger chamber of the second cylinder, and the plunger is configured to block the bypass when the plunger chamber passes the high-pressure refrigerant And opening the bypass hole when the plunger chamber passes the low-pressure refrigerant, so that part of the gas sucked into the second cylinder passes through the bypass hole Two intake ports.

According to the compressor of the embodiment of the present disclosure, the first cylinder adopts a vane groove pressure unloading mode, and the second cylinder adopts a plunger bypass unloading mode. This allows the compressor to operate in both variable and independent compression modes, which can be subdivided into six different operating modes. In this way, the independent compression can improve the cooling/heating efficiency of specific working conditions and the advantages of variable capacity can greatly improve the seasonal energy efficiency, the working mode is flexible, the energy saving effect is good, and the environment adaptability is strong.

An air conditioning system according to an embodiment of the second aspect of the present disclosure includes: the compressor; a reversing valve group, the reversing valve group and the exhaust port, the first intake port, and the second intake port a port, the plunger chamber, and the vane chamber are connected to supply any one of a low pressure refrigerant, an intermediate pressure refrigerant or a high pressure refrigerant, so that the compression member can be in a variable capacity working mode and independently compressed Switching between working modes; an outdoor heat exchanger, one end of the outdoor heat exchanger is connected to the reversing valve group; a first throttling element, one end of the first throttling element and the outdoor heat exchanger Connected to the other end; a flasher having an inlet, an exhaust port and a drain port, the inlet of the flasher being connected to the other end of the first throttle element, the exhaust port being used for The reversing valve group supplies an intermediate pressure refrigerant to the compressor; a second throttling element, one end of the second throttling element is connected to a liquid discharge port of the flasher; an indoor heat exchanger, the One end of the indoor heat exchanger is connected to the other end of the second throttle element, and the indoor exchange The other end is connected to said compressor through said valve group.

According to an air conditioning system of an embodiment of the present disclosure, the switching valve group includes first to third four-way valves for communicating high-pressure refrigerant to a slider chamber of the first cylinder and The low pressure refrigerant is supplied to the first suction port and the communication plunger chamber, and the second four-way valve is used to supply the medium pressure refrigerant to the second suction port, the compressor is in an independent compression operation mode When the first four-way valve is used to connect the low-pressure refrigerant to the vane chamber of the first cylinder and supply the high-pressure refrigerant to the first intake port and the communication plunger chamber, and the second four-way valve When the low pressure refrigerant is supplied to the second intake port, the compressor is in a single cylinder variable capacity working mode in which the first cylinder is not working and the second cylinder compression chamber is all engaged in compression; when the first four-way valve is used Connecting the high pressure refrigerant to the vane chamber of the first cylinder and supplying the low pressure refrigerant to the first intake port and the communication plunger chamber, and the second four-way valve for supplying the low pressure refrigerant to the second suction At the gas port, the compressor is in a two-cylinder variable capacity mode of operation; the third four-way valve To the control switch to cooling mode or a heating mode.

In some embodiments, the first four-way valve has first to fourth interfaces, the first interface is connected to the housing, and the second interface is connected to the first slider chamber, The third interface is configured to pass the low-pressure refrigerant, the fourth interface is respectively connected to the first air inlet and the plunger chamber, and the first four-way valve is configured to be in the first communication state and the second The first state is connected to the second interface, the third interface is connected to the fourth interface, and the compression chamber of the first cylinder is all involved in compression and The compression chamber portion of the two cylinders participates in compression, in the second communication state, the first interface is connected to the fourth interface, the second interface is connected to the third interface, and the first cylinder does not participate in compression and The compression chamber of the second cylinder is all involved in compression.

In some embodiments, the second four-way valve has first to fourth connection ports, wherein the fourth connection port is always closed, and the first connection port and the third interface of the first four-way valve Connected, the second connection port is connected to the second air inlet, the third connection port is connected to the flasher, and the second four-way valve is configured to be in the first communication state and the first The two connected states are switchable; in the first connected state, the first connecting port and the fourth connecting port are closed, the second connecting port is connected to the third connecting port, and the compression component is switchable to independent In the compressed working mode, the third connecting port and the fourth connecting port are closed in the second connected state, the first connecting port is connected to the second connecting port, and the compression component is switchable to the variable capacity working mode.

Optionally, the second four-way valve may be a three-way valve, and the three interfaces of the three-way valve respectively correspond to the first to third connection ports of the second four-way valve.

Optionally, the second four-way valve comprises two shut-off valves, wherein one end of one shut-off valve is formed as a first connecting port and one end of the other shut-off valve is formed as a third connecting port, and the other end of the two shut-off valves Connected and formed together as a second connection port.

Optionally, the second four-way valve comprises a shut-off valve and a one-way valve, wherein one end of the shut-off valve is formed as a first connecting port and one end of the one-way valve is formed as a third connecting port, and the other end of the shut-off valve Connected to the other end of the one-way valve and formed together as a second connection port, the one-way valve is electrically connected from the other end of the one-end valve.

In some embodiments, the third four-way valve has first to fourth flow ports, the first flow port is connected to the exhaust port, and the second flow port is for connecting to an outdoor heat exchanger. The third flow port, the first connection port, and the third interface are in communication with each other, the fourth flow port is for connecting with an indoor heat exchanger, and the third four-way valve is configured to be The first communication state and the second communication state are switchable; in the first communication state, the first flow port is connected to the second flow port, and the third flow port is connected to the fourth flow port, The compression chamber of the first cylinder is all engaged in compression and the compression chamber portion of the second cylinder is involved in compression, and in the second communication state, the first flow port is connected to the fourth flow port, the second flow port is The third flow port is connected, the first cylinder does not participate in compression and the compression chamber of the second cylinder is all involved in compression.

In some embodiments, a gas-liquid separator is further included, an inlet of the gas-liquid separator is connected to a third flow port of the third four-way valve, and an outlet of the gas-liquid separator is respectively associated with the first The third interface of the four-way valve and the first connection port of the second four-way valve are connected.

According to an air conditioning system according to an embodiment of the present disclosure, in the independent compression operation mode, the volume of the compression chamber when the second cylinder portion participates in compression is V2', and the volume of the compression chamber in the first cylinder is V1, which satisfies :V2'/V1=5%-30%.

According to an air conditioning system according to an embodiment of the present disclosure, in the variable volume operation mode, the volume of the compression chamber is V2 when the second cylinder is all engaged in compression, and the volume of the compression chamber in the first cylinder is V1, which satisfies: V2/V1 = 30% - 70%.

An air conditioning system according to an embodiment of the third aspect of the present disclosure includes: the compressor; a reversing valve group, the reversing valve group and the exhaust port, the first intake port, and the second suction a port, the plunger chamber, and the vane chamber are connected to supply any one of a low pressure refrigerant, an intermediate pressure refrigerant or a high pressure refrigerant, so that the compression member can be in a variable capacity mode of operation and independent Switching between compression working modes; an outdoor heat exchanger, one end of the outdoor heat exchanger is connected to the reversing valve group; a first throttling element, one end of the first throttling element and the outdoor heat exchange The other end of the apparatus is connected; the economizer has a first inlet, a second inlet, an exhaust port and a liquid discharge port, and the first inlet of the economizer is connected to the other end of the first throttle element a second inlet of the economizer is connected to the other end of the outdoor heat exchanger, the exhaust port is for supplying medium pressure refrigerant to the compressor through the reversing valve group; An element, one end of the second throttle element being connected to a drain of the economizer; External heat exchanger, one end of the outdoor heat exchanger and said second throttle element connected to the other end, the other end of the outdoor heat exchanger connected to the valve group through a compressor.

According to an air conditioning system of an embodiment of the present disclosure, the reversing valve group includes first to third four-way valves for correspondingly supplying a low-pressure refrigerant and an intermediate-pressure refrigerant to a first cylinder a vane chamber, a first suction port and a plunger chamber to allow the compression chamber of the first cylinder to participate in compression and the compression chamber portion of the second cylinder to participate in the compression of the first gear and only the second cylinder The compression chamber is all switched between the second gear position of the compression, and the second four-way valve is for supplying the medium pressure refrigerant or the low pressure refrigerant to the second suction port, so that the compressor works in independent compression Switching between a mode and a varactor compression operating mode, the third four-way valve is used to control switching to a cooling mode or a heating mode.

In some embodiments, the first four-way valve has first to fourth interfaces, the first interface is connected to the housing, and the second interface is connected to the first slider chamber, The third interface is configured to pass the low-pressure refrigerant, the fourth interface is respectively connected to the first air inlet and the plunger chamber, and the first four-way valve is configured to be in the first communication state and the second The first state is connected to the second interface, the third interface is connected to the fourth interface, and the compression chamber of the first cylinder is all involved in compression and The compression chamber portion of the two cylinders participates in compression, in the second communication state, the first interface is connected to the fourth interface, the second interface is connected to the third interface, and the first cylinder does not participate in compression and The compression chamber of the second cylinder is all involved in compression.

In some embodiments, the second four-way valve has first to fourth connecting ports, and the first connecting port is connected to the third interface of the first four-way valve, and the second connecting port is a second suction port connected to the economizer, the second four-way valve being configured to be switchable between a first communication state and a second communication state; The first connection port and the fourth connection port are closed in a connected state, the second connection port is connected to the third connection port, the compression component can be switched to an independent compression working mode, and in the second communication state The third connecting port and the fourth connecting port are closed, the first connecting port is connected to the second connecting port, and the compression component is switchable to a variable capacity working mode.

Optionally, the second four-way valve is a three-way valve, and three interfaces of the three-way valve are respectively formed as the first connection port to the third connection port.

Optionally, the second four-way valve comprises two shut-off valves, wherein one end of one shut-off valve is formed as a first connecting port and one end of the other shut-off valve is formed as a third connecting port, and the other end of the two shut-off valves Connected and formed together as a second connection port.

Optionally, the second four-way valve comprises a shut-off valve and a one-way valve, wherein one end of the shut-off valve is formed as a first connecting port and one end of the one-way valve is formed as a third connecting port, and the other end of the shut-off valve Connected to the other end of the one-way valve and formed together as a second connection port, the one-way valve is electrically connected from the other end of the one-end valve.

In some embodiments, the third four-way valve has first to fourth flow ports, the first flow port is connected to the exhaust port, and the second flow port is for connecting to an outdoor heat exchanger. The third flow port, the first connection port, and the third interface are in communication with each other, the fourth flow port is for connecting with an indoor heat exchanger, and the third four-way valve is configured to be The first communication state and the second communication state are switchable; in the first communication state, the first flow port is connected to the second flow port, and the third flow port is connected to the fourth flow port, The compression chamber of the first cylinder is all engaged in compression and the compression chamber portion of the second cylinder is involved in compression, and in the second communication state, the first flow port is connected to the fourth flow port, the second flow port is The third flow port is connected, the first cylinder does not participate in compression and the compression chamber of the second cylinder is all involved in compression.

In some embodiments, a gas-liquid separator is further included, an inlet of the gas-liquid separator is connected to a third flow port of the third four-way valve, and an outlet of the gas-liquid separator is respectively associated with the first The third interface of the four-way valve and the first connection port of the second four-way valve are connected.

According to an air conditioning system according to an embodiment of the present disclosure, in the independent compression operation mode, the volume of the compression chamber in which the second cylinder portion participates in compression is V2', and the volume of the compression chamber in the first cylinder is V1, which satisfies :V2'/V1=5%-30%.

According to an air conditioning system according to an embodiment of the present disclosure, in the variable volume operation mode, the volume of the compression chamber in which the second cylinder is all engaged in compression is V2, and the volume of the compression chamber in the first cylinder is V1, which satisfies: V2/V1 = 30% - 70%.

The additional aspects and advantages of the present disclosure will be set forth in part in the description which follows.

DRAWINGS

The above and/or additional aspects and advantages of the present disclosure will become apparent and readily understood from

FIG. 1 is a schematic view of an air conditioning system according to a first embodiment of the present disclosure.

2 is a schematic diagram of an air conditioning system operating in an independent compression cooling mode in accordance with a first embodiment of the present disclosure.

3 is a schematic diagram of an air conditioning system operating in an independent compression heating mode in accordance with a first embodiment of the present disclosure.

4 is a schematic diagram of an air conditioning system operating in a variable capacity (single cylinder) cooling mode according to a first embodiment of the present disclosure.

5 is a schematic diagram of an air conditioning system operating in a variable capacity (single cylinder) heating mode according to a first embodiment of the present disclosure.

6 is a schematic diagram of an air conditioning system operating in a variable capacity (two-cylinder) cooling mode according to a first embodiment of the present disclosure.

7 is a system flow diagram of an air conditioning system operating in a variable capacity (two-cylinder) heating mode in accordance with a first embodiment of the present disclosure.

8 is a schematic view of an air conditioning system according to a second embodiment of the present disclosure (replacement of the second four-way valve of the first embodiment with two shutoff valves).

9 is a schematic diagram of an air conditioning system (replacement of a second four-way valve of the first embodiment with a shut-off valve and a one-way valve) according to a third embodiment of the present disclosure.

10 is a schematic diagram of an air conditioning system operating in a cooling mode according to a fourth embodiment of the present disclosure (replacement of the flasher of the first embodiment with an economizer).

11 is a schematic diagram of an air conditioning system operating in a heating mode according to a fourth embodiment of the present disclosure (replacement of the flasher of the first embodiment with an economizer).

Reference mark:

Air conditioning system 100,

Compressor 1, exhaust port 1d, motor 2, first cylinder 3, first intake port 3s, first exhaust port 3d, vane chamber 3c, second cylinder 4, second intake port 4s, second Exhaust port 4d, plunger chamber 4c, first four-way valve 5, first interface 5d, second interface 5c, third interface 5s, fourth interface 5e, second four-way valve 6, first connection port 6c, Second connection port 6s, third connection port 6e, fourth connection port 6d, gas-liquid separator 7, third four-way valve 8, first flow port 8d, second flow port 8c, third flow port 8s, Four flow port 8e, outdoor heat exchanger 9, outdoor fan 10, first throttle element 11, flasher 12, first communication port 12c, second communication port 12a, third communication port 12b, second throttle element 13 , indoor heat exchanger 14, indoor fan 15, first shutoff valve 16, second shutoff valve 17, check valve 18, economizer 20, first port 20a, third port 20c, second port 20b, The fourth port 20d.

Detailed ways

The embodiments of the present disclosure are described in detail below, and the examples of the embodiments are illustrated in the drawings, wherein the same or similar reference numerals are used to refer to the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are intended to be illustrative only, and are not to be construed as limiting.

As shown in FIG. 1, a compressor 1 according to an embodiment of the first aspect of the present disclosure includes a housing, a compression member, and a reversing valve group, the housing having an exhaust port 1d, and the compression member including a first cylinder 3 and a second cylinder 4. The first sliding piece, the second sliding piece, the first piston and the second piston, the first cylinder 3 has a first air inlet 3s, a first exhaust port 3d and a sliding slot, and the first sliding piece is located in the sliding piece A portion of the groove and the slider groove located at the back of the first slider is formed as a slider chamber 3c, and the first slider is configured to be pressed against the first piston and in the slider when the slider chamber 3c passes the high-pressure refrigerant The chamber 3c is detached from the first piston when it passes through the low pressure refrigerant.

The second cylinder 4 has a second intake port 4s, a second exhaust port 4d, a plunger chamber 4c and a bypass hole. The plunger chamber 4c is disposed on the intermediate partition plate or the sub-bearing of the second cylinder 4, and the plunger chamber 4c is provided with a plunger configured to block the bypass hole when the plunger chamber 4c passes the high-pressure refrigerant and open the bypass hole when the plunger chamber 4c passes the low-pressure refrigerant, thereby sucking the second cylinder 4 Part of the gas passes through the bypass hole and bypasses the second suction port 4s (not shown).

According to the compressor 1 of the embodiment of the present disclosure, the first cylinder 3 adopts a vane groove pressure unloading mode, and the second cylinder adopts a plunger bypass unloading mode. Therefore, the compressor 1 can be operated in two ways of variable volume and independent compression, and can be subdivided into six different working modes. In this way, the independent compression can improve the cooling/heating efficiency of specific working conditions and the advantages of variable capacity can greatly improve the seasonal energy efficiency, the working mode is flexible, the energy saving effect is good, and the environment adaptability is strong.

As shown in FIG. 1 , an air conditioning system 100 according to an embodiment of the first aspect of the present disclosure includes: the compressor 1 , the reversing valve group, the outdoor heat exchanger 9 , the first throttle element 11 , the flasher 12 , The second throttle element 13 and the indoor heat exchanger 14.

The reversing valve group is connected to the exhaust port 1d, the first intake port 3s, the second intake port 4s, the plunger chamber 4c, and the vane chamber 3c to supply low-pressure refrigerant, medium-pressure refrigerant or high-pressure refrigerant Either of these allows the compression component to switch between a variable capacity mode of operation and an independent compression mode of operation.

One end of the outdoor heat exchanger 9 is connected to the reversing valve group, and one end of the first throttle element 11 is connected to the other end of the outdoor heat exchanger 9, and the flasher 12 has a first communication port 12c, a second communication port 12a, and a a three-port 12b, the first communication port 12c of the flasher 12 is connected to the other end of the first throttle element 11, and the second communication port 12a is for supplying the compressor 1 with medium-pressure refrigerant through the reversing valve group, and second One end of the throttle element 13 is connected to the third communication port 12b of the flasher 12, one end of the indoor heat exchanger 14 is connected to the other end of the second throttle element 13, and the other end of the indoor heat exchanger 14 is passed through the reversing valve group. It is connected to the compressor 1.

It can be understood that the reversing valve group can be a valve group composed of a plurality of four-way valves, which are directly or indirectly connected to each other and correspond to respective interfaces on the compressor 1 (including but not limited to the exhaust port 1d). The first suction port 3s, the second suction port 4s, the plunger chamber 4c, and the bypass hole are connected to make the compressor 1 selectively in a variable capacity condition or an independent compression condition.

For the first cylinder 3, when the reversing valve group supplies the high pressure refrigerant to the vane chamber 3c, the first vane is pressed against the first piston, and at this time, the compression chamber of the first cylinder 3 participates in the compression, The volume of the compression chamber of one cylinder 3 is V1. On the contrary, when the reversing valve group supplies the low-pressure refrigerant to the vane chamber 3c, the first vane is disengaged from the first piston, and at this time, the compression chamber of the first cylinder 3 does not participate in the compression.

For the second cylinder 4, when the reversing valve group supplies the high pressure refrigerant to the plunger chamber 4c, the plunger blocks the bypass hole, and at this time, the compression chamber of the second cylinder 4 can all participate in the compression, and the second The volume of the compression chamber of the cylinder 4 is V2. On the contrary, when the reversing valve group supplies the low-pressure refrigerant to the plunger chamber 4c, the plunger falls and the bypass hole is in an open state, and part of the gas in the second cylinder 4 is returned to the suction of the compressor via the bypass hole. The port (not shown), at this time, only the partial volume V2' of the compression chamber of the second cylinder 4 participates in compression.

Therefore, when the cooling or heating load is large, the compressor 1 operates in a two-cylinder full capacity mode to meet the requirements of indoor cold and heat load; when the cooling or heating load is small, the compressor 1 changes in a single cylinder. The capacity mode operates to reduce the number of starts and stops of the compressor 1, and improve the seasonal energy efficiency of the air conditioning system 100; under other conditions, the compressor 1 operates in an independent compression mode to improve the cooling or heating efficiency under specific operating conditions.

As a preferred embodiment, the reversing valve group includes a first four-way valve 5, a second four-way valve 6, and a third four-way valve 8, when the first four-way valve 5 is used to communicate high-pressure refrigerant to the first cylinder 3. The slide chamber 3c and the low pressure refrigerant are supplied to the first intake port 3s and the communication plunger chamber 4c, and the second four-way valve 6 is used to supply the intermediate pressure refrigerant to the second intake port 4s, the compressor It is in independent compression mode.

When the first four-way valve 5 is used to connect the low-pressure refrigerant to the vane chamber 3c of the first cylinder 3 and supply the high-pressure refrigerant to the first intake port 3s and the communication plunger chamber 4c, and the second four-way valve 6 When the low-pressure refrigerant is supplied to the second intake port 4s, the compressor is in a single-cylinder variable-capacity operation mode in which the first cylinder 3 does not operate and the second cylinder 4 compression chamber is all engaged in compression.

When the first four-way valve 5 is used to connect the high-pressure refrigerant to the vane chamber 3c of the first cylinder 3 and supply the low-pressure refrigerant to the first intake port 3s and the communication plunger chamber 4c, and the second four-way valve 6 When the low pressure refrigerant is supplied to the second intake port 4s, the compressor is in the two-cylinder variable capacity operation mode.

The third four-way valve 8 is used to control switching to the cooling mode or the heating mode.

Thereby, by the switching of the communication states of the first four-way valve 5, the second four-way valve 6, and the third four-way valve 8, the commutation of the liquid path in the air-conditioning system 100 is realized, so that the air-conditioning system 100 can work separately. In 6 specific operating modes: independent compression cooling mode, independent compression heating mode, variable capacity (single cylinder) cooling mode, variable capacity (single cylinder) heating mode, variable capacity (double cylinder) cooling mode, variable capacity ( Double cylinder) heating mode.

In some embodiments, the first four-way valve 5 has first to fourth interfaces, the first interface 5d is connected to the inside of the housing, the second interface 5c is connected to the slider chamber 3c, and the third interface 5s is for passing the low-pressure refrigerant The fourth port 5e is connected to the first air inlet 3s and the plunger chamber 4c, respectively, and the first four-way valve 5 is configured to be switchable between the first communication state and the second communication state. In the first communication state, the first interface 5d is connected to the second interface 5c, the third interface 5s is connected to the fourth interface 5e, the compression chambers of the first cylinder 3 are all involved in compression, and the compression chamber portion of the second cylinder 4 is involved in compression; In the second communication state, the first interface 5d is connected to the fourth interface 5e, the second interface 5c is connected to the third interface 5s, the first cylinder 3 does not participate in compression and the compression chambers of the second cylinder 4 all participate in compression.

In some embodiments, the second four-way valve 6 has first to fourth connection ports, the first connection port 6c is connected to the third interface 5s of the first four-way valve 5, and the second connection port 6s and the second suction port The port 4s is connected, the third port 6e is for connection with the second communication port 12a, and the second four-way valve 6 is configured to be switchable between the first communication state and the second communication state. In the first communication state, the first connection port 6c and the fourth connection port 6d are closed, the second connection port 6s is connected to the third connection port 6e, the compression component can be switched to the independent compression operation mode, and the third communication state is the third connection state. The connection port 6e and the fourth connection port 6d are closed, the first connection port 6c is connected to the second connection port 6s, and the compression member is switchable to the variable capacity operation mode.

The second four-way valve 6 is optionally a three-way valve, and the three interfaces of the three-way valve respectively correspond to the first to third connection ports 6c to 6e of the second four-way valve 6.

Of course, the present disclosure is not limited thereto. In the second aspect embodiment shown in FIG. 8, the second four-way valve 6 may be replaced by two shut-off valves, one end of which is formed as the first connecting port 6c and One end of the other shutoff valve is formed as a third connection port 6e, and the other ends of the two shutoff valves are connected and collectively formed as a second connection port 6s.

In the third aspect embodiment shown in FIG. 9, the second four-way valve 6 includes a shutoff valve and a one-way valve, wherein one end of the one-way valve is formed as a first connection port 6c and one end of the shut-off valve is formed as a third connection The port 6e has the other end of the shutoff valve connected to the other end of the check valve and formed together as a second connecting port 6s, and the one-way valve is electrically connected from one end to the other end.

As shown in FIG. 1, the third four-way valve 8 has first to fourth flow ports 8e, the first flow port 8d is connected to the second communication port 12a, and the second flow port 8c is for connecting to the outdoor heat exchanger 9. The third flow port 8s, the first connection port 6c, and the third port 5s are in communication with each other, the fourth flow port 8e is for connecting with the indoor heat exchanger 14, and the third four-way valve 8 is configured to be in the first communication state and The second communication state is switchable. In the first communication state, the first flow port 8d is connected to the second flow port 8c, the third flow port 8s is connected to the fourth flow port 8e, and the first flow is connected in the second communication state. The port 8d is connected to the fourth flow port 8e, and the second flow port 8c is connected to the third flow port 8s.

The first to third four-way valves may be solenoid-controlled electromagnetic four-way valves, which are in a first communication state when the coil is powered off and in a second communication state when the coil is powered. It can also be a four-way valve that is controlled by air pressure, hydraulic pressure or even manual control.

Further, a gas-liquid separator 7 is further included, the inlet of the gas-liquid separator 7 is connected to the third flow port 8e of the third four-way valve 8, and the outlet of the gas-liquid separator 7 is respectively the third of the first four-way valve 5 The interface 5s and the first connection port 6c of the second four-way valve 6 are connected.

According to an air conditioning system 100 according to an embodiment of the present disclosure, in the independent compression mode of operation, the volume of the compression chamber partially engaged in compression by the second cylinder 4 is V2', and the volume of the compression chamber in the first cylinder 3 is V1, which satisfies: V2'/V1 = 5%-30%.

According to an air conditioning system 100 according to an embodiment of the present disclosure, in the variable volume operation mode, the volume of the compression chamber in which the second cylinder 4 is all involved in compression is V2, and the volume of the compression chamber in the first cylinder 3 is V1, which satisfies: V2 /V1=30%-70%.

An air conditioning system 100 according to an embodiment of the fourth aspect of the present disclosure includes: the compressor 1 in the above embodiment, the outdoor heat exchanger 9, the first throttle element 11, the economizer 20, the second throttle element 13, and the indoor exchange Heater 14. One end of the outdoor heat exchanger 9 is connected to the reversing valve group, one end of the first throttling element 11 is connected to the other end of the outdoor heat exchanger 9, and the economizer 20 has a first port 20a, a third port 20c, and a The second port 20b and the fourth port 20d, the first port 20a of the economizer is connected to the other end of the first throttle element 11, and the third port 20c of the economizer 20 is connected to the other end of the outdoor heat exchanger 9. The second port 20b is for supplying the compressor 1 with the intermediate pressure refrigerant through the reversing valve group, and one end of the second throttle element 13 is connected to the fourth port 20d of the economizer 20, and one end of the indoor heat exchanger 14 Connected to the other end of the second throttle element 13, the other end of the indoor heat exchanger 14 is connected to the compressor 1 via a reversing valve block.

This embodiment differs from the second aspect embodiment in that the flasher is replaced with an economizer to further broaden the range of application of the air conditioning system 100.

The air conditioning system 100 according to the first to fourth embodiments of the present disclosure will be described in detail below with reference to FIGS. 1 through 11.

First embodiment

As shown in FIG. 1, an air conditioning system 100 according to a first embodiment of the present disclosure is composed of a compressor 1, a first four-way valve 5, a second four-way valve 6, a gas-liquid separator 7, a third four-way valve 8, and an outdoor The heat exchanger 9, the outdoor fan 10, the first throttle element 11, the flasher 12, the second throttle element 13, the indoor heat exchanger 14, and the indoor fan 15 are comprised. The compressor 1 is provided with a motor 2, a first cylinder 3 and a second cylinder 4. The motor 2, the first cylinder 3 and the second cylinder 4 are mounted on the same crankshaft. When the rotor of the motor 2 rotates, the rotors of the first cylinder 3 and the second cylinder 4 are driven to rotate, so that the first cylinder 3 and the second cylinder The interior of 4 achieves compression of the refrigerant gas.

The first four-way valve 5 has four interfaces, which are a first interface 5d, a second interface 5c, a third interface 5s and a fourth interface 5e. When the first four-way valve 5 is in the first communication state, the first interface 5d and the second interface 5c are in communication, and the third interface 5s is in communication with the fourth interface 5e; when the first four-way valve 5 is in the second communication state, The first interface 5d is in communication with the fourth interface 5e, and the third interface 5s is in communication with the second interface 5c.

The second four-way valve 6 has four connection ports, which are a first connection port 6c, a second connection port 6s, a third connection port 6e and a fourth connection port 6d, wherein the fourth connection port 6d is always closed. When the second four-way valve 6 is in the first communication state, the second connection port 6s and the third connection port 6e are in communication, the first connection port 6c and the fourth connection port 6d are in a closed state; when the second four-way valve 6 is at In the second communication state, the second connection port 6s communicates with the first connection port 6c, and the third connection port 6e and the fourth connection port 6d are in a closed state.

The third four-way valve 8 has four ports, which are a first flow port 8d, a second flow port 8c, a third flow port 8s, and a fourth flow port 8e. When the third four-way valve 8 is in the first communication state, the first flow port 8d and the second flow port 8c are in communication, the third flow port 8s is in communication with the fourth flow port 8e; when the third four-way valve 8 is in the second In the connected state, the first flow port 8d and the fourth flow port 8e communicate with each other, and the third flow port 8s and the second flow port 8c communicate with each other.

The first cylinder 3 is a cylinder that can determine whether it is working by controlling the pressure of the slider chamber 3c. The first cylinder 3 has a first intake port 3s, a first exhaust port 3d, and a vane chamber 3c. The first intake port 3s communicates with the fourth port 5e of the first four-way valve 5, the first exhaust port 3d communicates with the internal space of the compressor 1, and the vane chamber 3c is led out to the outside of the compressor 1 through the pipe. And connected to the second interface 5c of the first four-way valve 5. Unlike the cylinder configuration of the conventional compressor 1, there is no spring in the vane groove of the first cylinder 3. When the sliding vane chamber 3c is open to high pressure, the sliding vane of the first cylinder 3 is pressed against the rotor in the cylinder (not shown), at which time the first cylinder 3 can work normally (involved in gas compression), when slipping When the cavity 3c is open to a low pressure, the slider of the first cylinder 3 cannot press the rotor (not shown) in the cylinder, and at this time, the first cylinder 3 does not operate (cannot participate in gas compression). When the first cylinder 3 participates in gas compression, the gas is sucked by the first intake port 3s, and the compressed gas is discharged into the casing of the compressor 1 through the first exhaust port 3d, and through the exhaust port 1d of the compressor 1. The compressor 1 is discharged. When the first cylinder 3 participates in gas compression, its entire compression chamber volume is represented by V1.

The second cylinder 4 is a cylinder that relies on a plunger to perform exhaust bypass to achieve partial load operation. The second cylinder 4 has a second intake port 4s, a second exhaust port 4d, and a plunger chamber 4c provided in the partition or sub-bearing of the cylinder. The second suction port 4s communicates with the second connection port 6s of the second four-way valve 6, the second exhaust port 4d communicates with the internal space of the compressor 1, and the plunger chamber 4c is led out to the outside of the compressor 1 through the pipe And connected to the fourth interface 5e of the first four-way valve 5. A plunger (not shown) is provided in the cavity of the plunger chamber 4c, and the plunger blocks the bypass hole (not shown) of the cylinder in the case where the plunger chamber 4c passes the high-pressure refrigerant.

When the plunger chamber 4c of the second cylinder 4 passes the high-pressure refrigerant, the plunger in the plunger chamber 4c moves upward under the pressure of the high-pressure gas to completely block the bypass hole of the first cylinder 3. At this time, the gas is sucked, compressed, and pressurized by the second intake port 4s, and then discharged into the casing of the compressor 1 through the second exhaust port 4d, and finally the compressor 1 is discharged through the exhaust port 1d of the compressor 1. In this case, the entire volume of the second cylinder 4 participates in gas compression, that is, the second cylinder 4 operates at full load. The volume of the compression chamber when the second cylinder 4 is operated at full load is represented by V2.

When the plunger chamber 4c of the second cylinder 4 passes the low-pressure refrigerant, the plunger in the plunger chamber 4c is dropped downward by the force of gravity, and the bypass hole of the second cylinder 4 is opened. At this time, after the gas refrigerant is sucked in by the second suction port 4s, part of the gas is directly bypassed from the bypass hole to the suction port of the compressor (the specific structure is not shown in the drawing), and the remaining gas is passed through. After the compression, it is discharged into the casing of the compressor 1 from the exhaust port 4d, and finally the compressor 1 is discharged through the exhaust port 1d of the compressor 1.

In this case, only the volume of the compression chamber from the bypass hole to the second exhaust port 4d in the second cylinder 4 participates in compression, and the compression chamber from the second suction port 4s to the bypass hole The volume does not participate in gas compression, i.e. the second cylinder 4 operates at partial load. The volume of the compression chamber participating in the compression of the second cylinder 4 during partial load operation is indicated by V2'.

The gas-liquid separator 7 functions as a gas-liquid separator, which can store a portion of the refrigerant liquid that has not evaporated from the heat exchanger, and ensures that the refrigerant sucked into the suction port of the cylinder is a gas, preventing the refrigerant from slamming.

The flasher 12 is a two-way flasher having a second communication port 12a, a third communication port 12b, and a first communication port 12c. The second communication port 12a communicates with the third connection port 6e of the second four-way valve 6, and the third communication port 12b is connected to the second throttle element 13, and the first communication port 12c is connected to the first throttle element 11. The liquid can enter from the third communication port 12b, and flows out from the first communication port 12c, and can also enter from the first communication port 12c and flow out from the third communication port 12b.

Different modes of operation of the air conditioning system 100 according to the first embodiment of the present disclosure will be described below with reference to FIGS. 2 through 7. Depending on the mode of operation of each of the four-way valves, the air conditioning system 100 shown in FIG. 1 can operate in six different operating modes, respectively.

(1) Independent compression cooling mode

As shown in FIG. 2, when the third four-way valve 8, the first four-way valve 5, and the second four-way valve 6 are both in the first communication state, the air conditioning system 100 operates in an independent compression cooling mode. At this time, the first flow port 8d of the third four-way valve 8 communicates with the second flow port 8c, the third flow port 8s communicates with the fourth flow port 8e, and the first port 5d and the second port of the first four-way valve 5 The interface 5c is in communication, the third interface 5s is in communication with the fourth interface 5e, the third connection port 6e of the second four-way valve 6 is in communication with the second connection port 6s, and the first connection port 6c and the fourth connection port 6d are closed.

In this mode of operation, the slider chamber 3c of the first cylinder 3 communicates with the interior of the housing of the compressor 1 since the second interface 5c communicates with the first interface 5d. Since the pressure inside the casing of the compressor 1 is the exhaust pressure, it means that the vane chamber 3c of the first cylinder 3 is in communication with the high pressure. At this time, the slider of the first cylinder 3 is pressed against the rotor in the cylinder (not shown), and the first cylinder 3 can operate normally (the entire volume of V1 participates in gas compression). The refrigerant gas is sucked by the first intake port 3s of the first cylinder 3, and is compressed and pressurized in the first cylinder 3 (pressure is Pd), and the first cylinder 3 is discharged from the first exhaust port 3d, and further through the row. The port 1d discharges the compressor 1. Then, the refrigerant gas enters the outdoor heat exchanger 9 through the first flow port 8d and the second flow port 8c of the third four-way valve 8. In the outdoor heat exchanger 9, the refrigerant gas releases heat to the air in the environment, the heat is forced away by the outdoor fan 10, and the refrigerant gas that releases the heat is condensed to become a refrigerant liquid. This refrigerant liquid flows through the first throttle element 11, the pressure is lowered, and part of the liquid is flashed to become a gas-liquid mixture, which flows into the flasher 12. In the flasher 12, the flashed gas-liquid mixture forms a gas-liquid two-phase layer. The liquid phase enters the indoor heat exchanger 14 after being subjected to secondary throttling and depressurization by the second throttling element 13 (pressure drop to Ps). In the indoor heat exchanger 14, the refrigerant evaporates and absorbs heat, absorbing heat in the indoor air forced by the indoor fan 15 to generate a cooling effect. The heat-absorbing refrigerant evaporates into a gas, passes through the fourth connection port 8e and the third connection port 8s of the third four-way valve 8, and enters the gas-liquid separator 7, where the droplets that may be entrained in the gas are filtered out. Then, it flows back to the first intake port 3s of the first cylinder 3. Since the plunger chamber 4c of the second cylinder 4 and the first suction port 3s of the first cylinder 3 are in communication, the plunger chamber 4c is in communication with the low pressure, and the bypass hole of the second cylinder 4 is in an open state, the second cylinder 4 Only part of the volume (V2') can participate in gas compression. The gas in the flasher 12 (pressure Pm) flows to the second of the second cylinder 4 via the second communication port 12a of the flasher 12, the third connection port 6e of the second four-way valve 6, and the second connection port 6s. The intake port 4s is compressed and boosted in the V2' portion of the second cylinder, and then discharged into the casing of the compressor 1 via the second exhaust port 4d, and finally, together with the exhaust of the first cylinder 3, through the exhaust. The port 1d is discharged to the outside of the compressor. This cycle.

In this mode, the outdoor heat exchanger 9 is in a state of condensation and heat release, the indoor heat exchanger 14 is in an evaporation heat absorption state, and the air conditioning system 100 is in a state of cooling the room. Further, since the first cylinder 3 compresses the gas in the low pressure Ps state, the second cylinder 4 compresses the gas in the intermediate pressure Pm state, and the two cylinders discharge the high pressure gas in the pressure Pd, and the first The exhaust of the cylinder 3 and the suction of the second cylinder 4 are not mixed, so this mode of operation is an independent compression refrigeration mode in which the first cylinder and the second cylinder portion volume work together.

(2) Independent compression heating mode

When the third four-way valve 8 is in the second communication state, the first four-way valve 5 and the second four-way valve 6 are in the first communication state, the air conditioning system 100 shown in FIG. 1 operates in the independent compression heating mode. The system flow at this time is shown in Figure 3. At this time, the first flow port 8d of the third four-way valve 8 communicates with the fourth flow port 8e, the third flow port 8s communicates with the second flow port 8c, and the first port 5d and the second port of the first four-way valve 5 The interface 5c is in communication, the third interface 5s is in communication with the fourth interface 5e, the third connection port 6e of the second four-way valve 6 is in communication with the second connection port 6s, and the other end of the first connection port 6c is closed.

In this mode of operation, the states of the first four-way valve 5, the second four-way valve 6, the first cylinder 3, and the second cylinder 4 are the same as the independent compression cooling mode, that is, the first cylinder 3 is all involved in gas compression, The two cylinders 4 only have a partial volume (V2') involved in gas compression. The difference from the independent compression refrigeration mode is only that the order in which the refrigerant flows through the outdoor heat exchanger 9 and the indoor heat exchanger 14 is different.

In this mode of operation, the slider chamber 3c of the first cylinder 3 communicates with the interior of the housing of the compressor 1 since the second interface 5c communicates with the first interface 5d. Since the pressure inside the casing of the compressor 1 is the exhaust pressure, it means that the vane chamber 3c of the first cylinder 3 is in communication with the high pressure. At this time, the slider of the first cylinder 3 is pressed against the rotor (not shown) in the cylinder, and the first cylinder 3 can operate normally (participating in gas compression). The refrigerant gas is sucked by the first intake port 3s of the first cylinder 3, and is compressed and pressurized in the first cylinder 3 (pressure is Pd), and the first cylinder 3 is discharged from the first exhaust port 3d, and further through the row. The port 1d discharges the compressor 1. The refrigerant gas discharged from the compressor 1 passes through the first flow port 8d and the fourth flow port 8e of the third four-way valve 8, and first enters the indoor heat exchanger 14. In the indoor heat exchanger 14, the refrigerant gas releases heat to the indoor air, and the heat is forced away by the indoor fan 15 to convect the air to heat the room. The refrigerant gas that emits heat is condensed and becomes a refrigerant liquid. This refrigerant liquid flows through the second throttle element 13, the pressure is lowered, and part of the liquid flashes out, becoming a gas-liquid mixture, and flows into the flasher 12. In the flasher 12, the flashed gas-liquid mixture forms a gas-liquid two-phase layer. The liquid phase enters the outdoor heat exchanger 9 after being subjected to secondary throttling and pressure reduction (pressure drop to Ps) through the first throttling element 11. In the outdoor heat exchanger 9, the refrigerant evaporates and absorbs heat, absorbing heat in the outdoor air forced by the outdoor fan 10. The heat-absorbing refrigerant evaporates into a gas, passes through the second flow port 8c and the third flow port 8s of the third four-way valve 8, and enters the gas-liquid separator 7, where the liquid droplets that may be entrained in the gas are filtered out. Then, it flows back to the first intake port 3s of the first cylinder 3. Since the plunger chamber 4c of the second cylinder 4 and the first suction port 3s of the first cylinder 3 are in communication, the plunger chamber 4c is in communication with the low pressure, and the bypass hole of the second cylinder 4 is in an open state, the second cylinder 4 Only part of the volume (V2') can participate in gas compression. The gas phase (pressure Pm) in the flasher 12 flows to the second port 2 of the second cylinder 4 via the second communication port 12a of the flasher 12, the third connection port 6e of the second four-way valve 6, and the second connection port 6s. The intake port 4s is compressed and boosted in the V2' portion of the second cylinder, and then discharged into the casing of the compressor 1 via the second exhaust port 4d, and finally, together with the exhaust of the first cylinder 3, through the exhaust. The port 1d is discharged to the outside of the compressor. This cycle.

In this mode of operation, the indoor heat exchanger 14 is in a condensation heat release state, the outdoor heat exchanger 9 is in an evaporation heat absorption state, and the air conditioning system 100 is in a state of heating the indoor side. Further, since the first cylinder 3 compresses the gas in the low pressure Ps state, the second cylinder 4 compresses the gas in the intermediate pressure Pm state, and the two cylinders discharge the high pressure gas in the pressure Pd, and the first The exhaust of the cylinder 3 and the suction of the second cylinder 4 are not mixed, so this mode of operation is an independent compression heating mode in which the first cylinder and the second cylinder portion volume work together.

(3) variable capacity (single cylinder) cooling mode

When the first four-way valve 5 and the second four-way valve 6 are in the second communication state, and the third four-way valve 8 is in the first communication state, the air conditioning system 100 shown in FIG. 1 operates in a variable capacity (single cylinder) Cooling mode, the system flow at this time is shown in Figure 4. At this time, the first flow port 8d of the third four-way valve 8 communicates with the second flow port 8c, the third flow port 8s communicates with the fourth flow port 8e, and the first port 5d and the fourth port of the first four-way valve 5 The interface 5e is in communication, the third interface 5s is in communication with the second interface 5c, the first connection port 6c of the second four-way valve 6 is in communication with the second connection port 6s, and the third connection port 6e and the fourth connection port 6d are closed.

In this mode of operation, since the second interface 5c and the third interface 5s are in communication, the fourth interface 5e communicates with the first interface 5d, so that the slider cavity 3c of the first cylinder 3 and the low pressure pipeline of the pressure Ps are connected. The first intake port 3s of the first cylinder 3 communicates with a high pressure in the housing of the compressor 1. At this time, the slider of the first cylinder 3 cannot press the rotor (not shown) in the cylinder, and at the same time, since the pressure of the first intake port 3s of the first cylinder 3 is equal to the exhaust pressure in the casing of the compressor 1, The rotor of the first cylinder 3 will idle and cannot participate in gas compression. Due to the high pressure communication between the plunger chamber 4c of the second cylinder 4 and the housing connected to the compressor 1, the plunger in the plunger chamber 4c rises under the action of the high pressure, blocking the bypass hole on the second cylinder 4, The entire volume of the second cylinder 4 (indicated by V2) is involved in gas compression. At this time, the refrigerant gas is sucked by the second intake port 4s, compressed and boosted in the second cylinder 4 (pressure is Pd), and the second cylinder 4 is discharged from the second exhaust port 4d, and further through the exhaust port. 1d discharges the compressor 1. Then, the refrigerant gas enters the outdoor heat exchanger 9 through the first flow port 8d and the second flow port 8c of the third four-way valve 8. In the outdoor heat exchanger 9, the refrigerant gas releases heat to the air in the environment, the heat is forced away by the outdoor fan 10, and the refrigerant gas that releases the heat is condensed to become a refrigerant liquid. This refrigerant liquid flows through the first throttle element 11, the pressure is lowered, and part of the liquid is flashed to become a gas-liquid mixture, which flows into the flasher 12. In the flasher 12, the flashed gas-liquid mixture forms a gas-liquid two-phase layer. Wherein the gas phase is blocked in the flasher 12 due to the disconnection of the third connection port 6e of the second four-way valve 6, and the liquid phase is depressurized by the second throttling element 13 (pressure drop to Ps), Enter the indoor heat exchanger 14. In the indoor heat exchanger 14, the refrigerant evaporates and absorbs heat, absorbing heat in the indoor air forced by the indoor fan 15 to generate a cooling effect. The heat-absorbing refrigerant evaporates into a gas, passes through the fourth communication port 8e and the third communication port 8s of the third four-way valve 8, and enters the gas-liquid separator 7, and filters out droplets that may be entrained in the gas. Then, it flows back to the second intake port 4s of the second cylinder 4 through the second connection port 6s of the second four-way valve 6 and the first connection port 6c. This cycle.

In this mode, the outdoor heat exchanger 9 is in a state of condensation and heat release, the indoor heat exchanger 14 is in an evaporation heat absorption state, and the air conditioning system 100 is in a state of cooling the room. Further, since the first cylinder 3 is in the inoperative mode, only the second cylinder 4 operates, which is a variable capacity operation with respect to the full capacity of the two cylinders, and thus the operation mode is a variable capacity (single cylinder) cooling mode.

(4) Variable capacity (single cylinder) heating mode

When the first four-way valve 5, the second four-way valve 6, and the third four-way valve 8 are both in the second communication state, the air conditioning system 100 shown in FIG. 1 operates in a variable capacity (single cylinder) heating mode. The system flow at this time is shown in Figure 5. At this time, the first flow port 8d of the third four-way valve 8 communicates with the fourth flow port 8e, the third flow port 8s communicates with the second flow port 8c, and the first port 5d and the fourth port of the first four-way valve 5 The interface 5e is in communication, the third interface 5s is in communication with the second interface 5c, the first connection port 6c of the second four-way valve 6 is in communication with the second connection port 6s, and the third connection port 6e and the fourth connection port 6d are closed.

In this mode of operation, the states of the first four-way valve 5, the second four-way valve 6, the first cylinder 3, and the second cylinder 4 are the same as the variable-capacity (single-cylinder) cooling mode, that is, the first cylinder 3 does not participate. The gas is compressed and the entire volume of the second cylinder 4 participates in gas compression. The difference from the variable capacity (single cylinder) cooling mode is only that the order in which the refrigerant flows through the outdoor heat exchanger 9 and the indoor heat exchanger 14 is different.

In this mode of operation, since the second interface 5c and the third interface 5s are in communication, the fourth interface 5e communicates with the first interface 5d, so that the slider cavity 3c of the first cylinder 3 and the low pressure pipeline of the pressure Ps are connected. The first intake port 3s of the first cylinder 3 communicates with a high pressure in the housing of the compressor 1. At this time, the slider of the first cylinder 3 cannot press the rotor (not shown) in the cylinder, and at the same time, since the suction pressure of the first cylinder 3 is equal to the exhaust pressure in the casing of the compressor 1, the first cylinder The rotor of 3 will idle and cannot participate in gas compression. Due to the high pressure communication between the plunger chamber 4c of the second cylinder 4 and the housing connected to the compressor 1, the plunger in the plunger chamber 4c rises under the action of the high pressure, blocking the bypass hole on the second cylinder 4, The entire volume of the second cylinder 4 (indicated by V2) is involved in gas compression. At this time, the refrigerant gas is sucked by the second intake port 4s of the second cylinder 4, compressed and pressurized in the second cylinder 4 (pressure is Pd), and the second cylinder 4 is discharged from the second exhaust port 4d. Further, the compressor 1 is discharged through the exhaust port 1d. Then, the refrigerant gas enters the indoor heat exchanger 14 through the first flow port 8d and the fourth flow port 8e of the third four-way valve 8. In the indoor heat exchanger 14, the refrigerant gas releases heat to the indoor air, and the heat is forced away by the indoor fan 15 to convect the air to supply heat to the room. The refrigerant gas that emits heat is condensed and becomes a refrigerant liquid. This refrigerant liquid flows through the second throttle element 13, the pressure is lowered, and part of the liquid flashes out, becoming a gas-liquid mixture, and flows into the flasher 12. In the flasher 12, the flashed gas-liquid mixture forms a gas-liquid two-phase layer. Wherein the gas phase is blocked in the flasher 12 due to the disconnection of the third connection port 6e of the second four-way valve 6, and the liquid phase is depressurized by the first throttling element 11 (pressure drop to Ps), Enter the outdoor heat exchanger 9. In the outdoor heat exchanger 9, the refrigerant evaporates and absorbs heat, absorbing heat in the outdoor air forced by the outdoor fan 10. The heat-absorbing refrigerant evaporates into a gas, passes through the second flow port 8c and the third flow port 8s of the third four-way valve 8, and enters the gas-liquid separator 7, where the liquid droplets that may be entrained in the gas are filtered out. Then, it flows back to the second intake port 4s of the second cylinder 4 through the first connection port 6c and the second connection port 6s of the second four-way valve 6. This cycle.

In this mode, the indoor heat exchanger 14 is in a condensation heat release state, the outdoor heat exchanger 9 is in an evaporation heat absorption state, and the air conditioning system 100 is in a state of heating the room. Further, since the first cylinder 3 is in the inoperative mode, only the second cylinder 4 operates, which is a variable capacity operation with respect to the full capacity of the two cylinders, and thus the operation mode is a variable capacity (single cylinder) heating mode.

(5) variable capacity (double cylinder) cooling mode

When the third four-way valve 8 and the first four-way valve 5 are in the first communication state, and the second four-way valve 6 is in the second communication state, the air conditioning system 100 shown in FIG. 1 operates in the variable capacity (two-cylinder) Cooling mode, the system flow at this time is shown in Figure 6. At this time, the first flow port 8d of the third four-way valve 8 communicates with the second flow port 8c, the third flow port 8s communicates with the fourth flow port 8e, and the first port 5d and the second port of the first four-way valve 5 The interface 5c is in communication, the third interface 5s is in communication with the fourth interface 5e, the first connection port 6c of the second four-way valve 6 is in communication with the second connection port 6s, and the third connection port 6e and the fourth connection port 6d are closed.

In this mode of operation, the slider chamber 3c of the first cylinder 3 communicates with the interior of the housing of the compressor 1 since the second interface 5c communicates with the first interface 5d. Since the pressure in the casing of the compressor 1 is the exhaust pressure, the vane chamber 3c of the first cylinder 3 is in communication with the high pressure, and the vane of the first cylinder 3 is pressed against the rotor in the cylinder (not shown). The first cylinder 3 can operate normally (participating in gas compression). Since the plunger chamber 4c of the second cylinder 4 and the first suction port 3s of the first cylinder 3 are in communication, the plunger chamber 4c communicates with the low pressure, the bypass hole of the second cylinder 4 is in an open state, and the second cylinder 4 Only part of the volume (V2') can participate in gas compression.

At this time, the refrigerant gas is sucked by the first intake port 3s of the first cylinder 3, compressed and pressurized in the first cylinder 3 (pressure is Pd), and the first cylinder 3 is discharged from the first exhaust port 3d. Further, the compressor 1 is discharged through the exhaust port 1d. At the same time, the gas is sucked by the second intake port 4s of the second cylinder 4, compressed and pressurized in the V2' portion of the second cylinder, and discharged into the casing of the compressor 1 via the second exhaust port 4d, and The exhaust gas of one cylinder 3 is discharged to the outside of the compressor 1 via the exhaust port 1d. The refrigerant gas discharged from the compressor 1 enters the outdoor heat exchanger 9 through the first flow port 8d and the second flow port 8c of the third four-way valve 8. In the outdoor heat exchanger 9, the refrigerant gas releases heat to the air in the environment, the heat is forced away by the outdoor fan 10, and the refrigerant gas that releases the heat is condensed to become a refrigerant liquid. This refrigerant liquid flows through the first throttle element 11, the pressure is lowered, and part of the liquid is flashed to become a gas-liquid mixture, which flows into the flasher 12. In the flasher 12, the flashed gas-liquid mixture forms a gas-liquid two-phase layer. Wherein the gas phase is blocked in the flasher 12 due to the disconnection of the third connection port 6e of the second four-way valve 6, and the liquid phase is depressurized by the second throttling element 13 (pressure drop to Ps), Enter the indoor heat exchanger 14. In the indoor heat exchanger 14, the refrigerant evaporates and absorbs heat, absorbing heat in the indoor air forced by the indoor fan 15 to generate a cooling effect. The heat-absorbing refrigerant evaporates into a gas, passes through the fourth flow port 8e and the third flow port 8s of the third four-way valve 8, and enters the gas-liquid separator 7, where the liquid droplets that may be entrained in the gas are filtered out. Then, it is divided into two paths, and the first path flows back to the first air inlet 3s of the first cylinder 3 through the third interface 5s and the fourth interface 5e, and the second road flows back through the first connection port 6c and the second connection port 6s. The second intake port 4s of the second cylinder 4. This cycle.

In this mode, the outdoor heat exchanger 9 is in a state of condensation and heat release, the indoor heat exchanger 14 is in an evaporation heat absorption state, and the air conditioning system 100 is in a state of cooling the room. Since the first cylinder 3 and the second cylinder 4 work simultaneously, they both inhale from the low pressure line of pressure Ps and exhaust to the high pressure line of pressure Pd, and the two cylinders are equivalent to the parallel operation mode, so this The working mode is a variable capacity (two-cylinder) cooling mode in which two cylinders work together.

(6) Variable capacity (double cylinder) heating mode

When the first four-way valve 5 is in the first communication state, the third four-way valve 8 and the second four-way valve 6 are in the second communication state, the air conditioning system 100 shown in FIG. 1 operates in the variable capacity (two-cylinder) Heating mode, the system flow at this time is shown in Figure 7. At this time, the first flow port 8d of the third four-way valve 8 communicates with the fourth flow port 8e, the third flow port 8s communicates with the second flow port 8c, and the first port 5d and the second port of the first four-way valve 5 The interface 5c is in communication, the third interface 5s is in communication with the fourth interface 5e, the first connection port 6c of the second four-way valve 6 is in communication with the second connection port 6s, and the third connection port 6e and the fourth connection port 6d are closed.

In this mode of operation, the slider chamber 3c of the first cylinder 3 communicates with the interior of the housing of the compressor 1 since the second interface 5c communicates with the first interface 5d. Since the pressure in the casing of the compressor 1 is the exhaust pressure, the vane chamber 3c of the first cylinder 3 is in communication with the high pressure, and the vane of the first cylinder 3 is pressed against the rotor in the first cylinder 3 (not shown) Out), the first cylinder 3 can work normally (involved in gas compression). At the same time, since the plunger chamber 4c of the second cylinder 4 and the suction port 3s of the first cylinder 3 are in communication, the plunger chamber 4c is in communication with the low pressure, the bypass hole of the second cylinder 4 is in an open state, and the second cylinder 4 is Only part of the volume (V2') can participate in gas compression.

At this time, the refrigerant gas is sucked by the first intake port 3s of the first cylinder 3, compressed and pressurized in the first cylinder 3 (pressure is Pd), and the first cylinder 3 is discharged from the first exhaust port 3d. Further, the compressor 1 is discharged through the exhaust port 1d. At the same time, the gas is sucked by the second intake port 4s of the second cylinder 4, compressed and pressurized in the V2' portion of the second cylinder, and discharged into the casing of the compressor 1 via the second exhaust port 4d, and The exhaust gas of one cylinder 3 is discharged to the outside of the compressor 1 via the exhaust port 1d. The refrigerant gas discharged from the compressor 1 enters the indoor heat exchanger 14 through the first flow port 8d and the fourth flow port 8e of the third four-way valve 8. In the indoor heat exchanger 14, the refrigerant gas releases heat to the indoor air, and the heat is forced away by the indoor fan 15 to convect the air to supply heat to the room. The refrigerant gas that emits heat is condensed and becomes a refrigerant liquid. This refrigerant liquid flows through the second throttle element 13, the pressure is lowered, and part of the liquid flashes out, becoming a gas-liquid mixture, and flows into the flasher 12. In the flasher 12, the flashed gas-liquid mixture forms a gas-liquid two-phase layer. Wherein the gas phase is blocked in the flasher 12 due to the disconnection of the third connection port 6e of the second four-way valve 6, and the liquid phase is depressurized by the first throttling element 11 (pressure drop to Ps), Enter the outdoor heat exchanger 9. In the outdoor heat exchanger 9, the refrigerant evaporates and absorbs heat, absorbing heat in the outdoor air forced by the outdoor fan 10. The heat-absorbing refrigerant evaporates into a gas, passes through the second flow port 8c and the third flow port 8s of the third four-way valve 8, and enters the gas-liquid separator 7, where the liquid droplets that may be entrained in the gas are filtered out. Then divided into two ways, the first way passes through the third interface 5s of the first four-way valve, the fourth interface 5e flows back to the first suction port 3s of the first cylinder 3, and the second path passes through the second four-way valve A connection port 6c and a second connection port 6s flow back to the second intake port 4s of the second cylinder 4. This cycle.

In this mode, the indoor heat exchanger 14 is in a condensation heat release state, the outdoor heat exchanger 9 is in an evaporation heat absorption state, and the air conditioning system 100 is in a state of heating the room. Since the first cylinder 3 and the second cylinder 4 work simultaneously, they both inhale from the low pressure line of pressure Ps and exhaust to the high pressure line of pressure Pd, and the two cylinders are equivalent to the parallel operation mode, so this The working mode is a variable capacity (two-cylinder) heating mode in which two cylinders work together.

In summary, the technical solution described in the present disclosure can implement independent compression and switching of the two-speed variable capacity operation mode. During independent compression operation, the cylinder volumes involved in compression are V1 and V2', respectively. When the two gears are in variable capacity operation, the two gear capacities are V2, V1+V2'.

As a preferred embodiment, the cylinder volume participating in the compression is defined as: when independently compressed, the volume of the compression chamber in which the second cylinder 4 partially participates in compression is 5%-30% of the volume of the compression chamber of the first cylinder 3, ie, V2'/V1= 5%-30%; during the variable capacity operation, the volume of all compression chambers in which the second cylinder 4 participates in compression is 30%-70% of the volume of the compression chamber of the first cylinder 3, that is, V2/V1=30%-70%.

Second embodiment

The second embodiment differs from the first embodiment in that the second four-way valve 6 in the first embodiment is replaced with other elements, and the overall realized function of the air conditioning system 100 is unchanged.

As shown in FIG. 8, the second four-way valve 6 in FIG. 1 is replaced by two shut-off valves (the first shut-off valve 16 and the second shut-off valve 17), and the same can be realized as shown in FIG. 1-7. The various functions of the system described.

In this solution, when the first shutoff valve 16 is turned on and the second shutoff valve 17 is closed, the third connecting port 6e and the second connecting port 6s are in communication at this time, and the first connecting port 6c and the second connecting port 6s are blocked. The second connection valve 6 is in the first communication state. When the first shutoff valve 16 is closed and the second shutoff valve 17 is turned on, the third connection port 6e and the second connection port 6s are blocked. A connection port 6c communicates with the second connection port 6s, which corresponds to the second four-way valve 6 being in the second communication state.

It can be understood that the air conditioning system 100 of the second embodiment of the present disclosure also has the above-mentioned functions of the air conditioning system 100 of the first embodiment, and can also operate in the above six working modes, and details are not described herein.

Third embodiment

The third embodiment differs from the first embodiment in that the second four-way valve 6 in the first embodiment is replaced with other elements, and the overall realized function of the air conditioning system 100 is unchanged.

As shown in FIG. 9, the second four-way valve 6 of FIG. 1 is replaced by a first shut-off valve 16 and a one-way valve, and the system described in FIGS. 1-7 can also be realized. Various functions. In this solution: when the first shutoff valve 16 is turned on, at this time, the third connection port 6e and the second connection port 6s are in communication, and the first connection port 6c and the second connection port 6s are blocked (due to the flasher 12) The pressure Pm is greater than the pressure Ps) of the gas-liquid separator 7, corresponding to the second four-way valve 6 being in the first communication state; when the first shut-off valve 16 is closed, the third connection port 6e and the second connection port 6s are blocked at this time. The first connecting port 6c and the second connecting port 6s are in communication, and the second four-way valve 6 is in the second communicating state.

It can be understood that the air conditioning system 100 of the third embodiment of the present disclosure also has the above-mentioned functions of the air conditioning system 100 of the first embodiment, and can also operate in the above six working modes, and details are not described herein.

Fourth embodiment

The fourth embodiment differs from the first embodiment in that the flasher 12 can be replaced with an economizer 20, and the various operating modes described above can be implemented as well. In other words, the flasher 12 can be replaced with the economizer 20, the connecting line is correspondingly fine-tuned, and the overall implemented function of the air conditioning system 100 is unchanged.

As shown in FIGS. 10 and 11, the economizer 20 is a hollow container having four ports (ie, a first port 20a, a second port 20b, a third port 20c, and a fourth port 20d), wherein A heat exchange tube is disposed between the third port 20c and the fourth port 20d, and the fluid in the heat exchange tube can exchange heat with the fluid of the hollow portion.

Fig. 10 is a schematic view showing the air conditioning system 100 of the fourth embodiment in a cooling mode. As shown in FIG. 10, in the cooling mode, the inlet of the first throttle element 11 is connected to the outdoor heat exchanger 9, and the outlet of the first throttle element 11 is connected to the first port 20a of the economizer 20, the second pass The port 20b is connected to the third connecting port 6e of the second four-way valve 6, the third port 20c is connected to the outdoor heat exchanger 9, and the fourth port 20d is connected to the inlet of the second throttle element 13, the second throttling The outlet of element 13 is connected to an outdoor heat exchanger 14.

At this time, the high-temperature high-pressure liquid refrigerant flowing out of the outdoor heat exchanger 9 is divided into two paths, the first passage is throttled by the first flow element 11 and enters the economizer 20, and the second passage directly enters the economy from the third through-port 20c. Heat exchange tube in the device 20. After the throttling, the first refrigerant flashes due to the pressure drop, and becomes a low-temperature low-pressure gas-liquid mixture. The low-temperature and low-pressure gas-liquid mixture cools the liquid refrigerant in the econductor heat exchange tube, so that the liquid refrigerant has a higher ratio. High subcooling can improve cooling capacity. The gas-liquid mixture of the first passage absorbs the heat of the second refrigerant liquid and evaporates, and enters the second portion of the second cylinder 4 through the third connection port 6e of the second four-way valve 6 and the second connection port 6s in a gaseous state. The suction port is 4s for independent compression operation. The liquid refrigerant having a higher degree of subcooling in the economizer 20 flows out of the economizer 20 through the fourth port 20d, passes through the second throttling element 13 and is throttled to enter the indoor heat exchanger 14, and the indoor heat exchanger Evaporation was completed in 14.

Figure 11 is a schematic view of the air conditioning system 100 of the fourth embodiment in a heating mode. As shown in FIG. 11, in the heating mode, the inlet of the first throttle element 11 is connected to the indoor heat exchanger 14, the outlet of the first throttle element 11 is connected to the first port 20a of the economizer 20, and the second The port 20b is connected to the third connection port 6e of the second four-way valve 6, the third port 20c is connected to the indoor heat exchanger 14, and the fourth port 20d is connected to the inlet of the second throttle element 13, the second section The outlet of the flow element 13 is connected to the outdoor heat exchanger 9.

At this time, the high-temperature and high-pressure liquid refrigerant flowing out of the indoor heat exchanger 14 is divided into two paths, the first passage is throttled by the first flow element 11 and enters the economizer 20, and the second passage directly enters the economy from the third through-port 20c. Heat exchange tube in the device 20. After the throttling, the first refrigerant flashes due to the pressure drop, and becomes a low-temperature low-pressure gas-liquid mixture. The low-temperature low-pressure gas-liquid mixture cools the liquid refrigerant in the heat exchange tube of the economizer 20 to make the liquid refrigerant. It has a higher degree of subcooling and can increase the heat absorption capacity of evaporation. The gas-liquid mixture of the first passage absorbs the heat of the second refrigerant liquid and evaporates, and enters the second portion of the second cylinder 4 through the third connection port 6e of the second four-way valve 6 and the second connection port 6s in a gaseous state. The suction port is 4s for independent compression operation. The liquid refrigerant having a higher degree of subcooling in the economizer 20 flows out of the economizer 20 from the fourth port 20d, passes through the second throttling element 13 and is throttled into the indoor heat exchanger 9, and is in the indoor heat exchanger. Evaporation was completed in 9.

It can be understood that the air conditioning system 100 of the fourth embodiment of the present disclosure also has the above-mentioned functions of the air conditioning system 100 of the first embodiment, and can also operate in the above six working modes, and details are not described herein.

In the description of the present disclosure, it is to be understood that the terms "upper", "lower", "front", "back", "top", "bottom", "inside", "outside", etc. indicate the orientation or position. The relationship is based on the orientation or positional relationship shown in the drawings, and is merely for the convenience of the description of the disclosure and the simplification of the description, and does not indicate or imply that the structure or element referred to has a specific orientation, is constructed and operated in a specific orientation, and thus It is not to be understood as limiting the disclosure. Furthermore, features defining "first" and "second" may include one or more of the features, either explicitly or implicitly. In the description of the present disclosure, "a plurality of" means two or more unless otherwise stated.

In the description of the present specification, the description with reference to the terms "one embodiment", "some embodiments", "illustrative embodiment", "example", "specific example", or "some examples", etc. Particular features, structures, materials or features described in the examples or examples are included in at least one embodiment or example of the present disclosure. In the present specification, the schematic representation of the above terms does not necessarily mean the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in a suitable manner in any one or more embodiments or examples.

While the embodiments of the present invention have been shown and described, it will be understood by those skilled in the art The scope of the disclosure is defined by the claims and their equivalents.

Claims (11)

A compressor, comprising: a housing having an exhaust port; a compression member, the compression member including a first cylinder, a second cylinder, a first slider, a second slider, a first piston, and a second piston, the first cylinder having a first intake port and a first exhaust a port and a sliding groove, the first sliding piece is located in the sliding groove, and a portion of the sliding groove located at a back of the first sliding piece is formed as a sliding cavity, and the first sliding piece is Constructed to be pressed against the first piston when the vane chamber is pressurized with high pressure refrigerant and disengaged from the first piston when the vane chamber is open to low pressure refrigerant, the second cylinder having a second a suction port, a second exhaust port, a plunger chamber and a bypass hole, wherein the plunger chamber is disposed on a middle partition plate or a sub-bearing of the second cylinder, and a plunger is disposed in the plunger chamber The plunger is configured to block the bypass hole when the plunger chamber passes the high pressure refrigerant and open the bypass hole when the plunger chamber opens the low pressure refrigerant to suck the second cylinder Part of the gas passes through the bypass hole and bypasses the second suction port. An air conditioning system, comprising: The compressor of claim 1; a reversing valve group, the reversing valve group is connected to the exhaust port, the first air inlet, the second air inlet, the plunger chamber, and the sliding chamber to supply a low voltage thereto Any one of a refrigerant, an intermediate pressure refrigerant or a high pressure refrigerant to enable the compression member to switch between a variable capacity mode of operation and an independent compression mode of operation; An outdoor heat exchanger, one end of the outdoor heat exchanger is connected to the reversing valve group; a first throttle element, one end of the first throttle element is connected to the other end of the outdoor heat exchanger; a flasher having a first communication port, a second communication port, and a third communication port, the first communication port of the flasher being connected to the other end of the first throttle element, the second communication a port for supplying medium pressure refrigerant to the compressor through the reversing valve group; a second throttle element, one end of the second throttle element is connected to a third communication port of the flasher; An indoor heat exchanger, one end of the indoor heat exchanger is connected to the other end of the second throttle element, and the other end of the indoor heat exchanger is connected to the compressor through the reversing valve group. An air conditioning system, comprising: The compressor of claim 1; a reversing valve group, the reversing valve group is connected to the exhaust port, the first air inlet, the second air inlet, the plunger chamber, and the sliding chamber to supply a low voltage thereto Any one of a refrigerant, an intermediate pressure refrigerant or a high pressure refrigerant to enable the compression member to switch between a variable capacity mode of operation and an independent compression mode of operation; An outdoor heat exchanger, one end of the outdoor heat exchanger is connected to the reversing valve group; a first throttle element, one end of the first throttle element is connected to the other end of the outdoor heat exchanger; An economizer having a first port, a second port, a third port, and a fourth port, the first port of the economizer being connected to the other end of the first throttle element, a second port of the economizer is connected to the other end of the outdoor heat exchanger, and the third port is configured to supply the compressor with an intermediate pressure refrigerant through the reversing valve group; a second throttle element, one end of the second throttle element is connected to the fourth port of the economizer; An indoor heat exchanger, one end of the indoor heat exchanger is connected to the other end of the second throttling element, and the other end of the indoor heat exchanger is connected to the compressor through the reversing valve block The air conditioning system according to claim 2 or 3, wherein the reversing valve group includes first to third four-way valves, When the first four-way valve is used to communicate high pressure refrigerant to a vane chamber of the first cylinder and to supply low pressure refrigerant to the first intake port and the communication plunger chamber, and the second four-way valve is used for When the medium pressure refrigerant is supplied to the second intake port, the compressor is in an independent compression mode of operation; When the first four-way valve is used to communicate low pressure refrigerant to a vane chamber of the first cylinder and to supply high pressure refrigerant to the first intake port and the communication plunger chamber, and the second four-way valve is used for When the low pressure refrigerant is supplied to the second intake port, the compressor is in a single cylinder variable capacity working mode in which the first cylinder is not working and the compression chamber of the second cylinder is all involved in compression; When the first four-way valve is used to communicate high pressure refrigerant to a vane chamber of the first cylinder and to supply low pressure refrigerant to the first intake port and the communication plunger chamber, and the second four-way valve is used for When the low pressure refrigerant is supplied to the second intake port, the compressor is in a two-cylinder varactor mode in which the first cylinder and the second cylinder participate in compression; The third four-way valve is used to control switching to a cooling mode or a heating mode. The air conditioning system according to claim 4, wherein The first four-way valve has first to fourth interfaces, the first interface is connected to the housing, the second interface is connected to the first sliding chamber, and the third interface is used for a low pressure refrigerant, the fourth interface being respectively connected to the first suction port and the plunger chamber, the first four-way valve being configured to be switchable between a first communication state and a second communication state ; The first interface is connected to the second interface, the third interface is connected to the fourth interface, and the first interface is connected to the fourth interface in the second connected state. The second interface is connected to the third interface. The air conditioning system according to claim 5, wherein the second four-way valve has first to fourth connecting ports, and the first connecting port is connected to the third interface of the first four-way valve. The second connection port is connected to the second air inlet, the third connection port is connected to the economizer or the flasher, the fourth interface is always closed, and the second four port The valve is configured to be switchable between the first communication state and the second communication state; The first connection port and the fourth connection port are closed in a first communication state, the second connection port is connected to the third connection port, and the third connection port and the second connection state are in a second communication state. The fourth connection port is closed, and the first connection port is connected to the second connection port. The air conditioning system according to claim 6, wherein the second four-way valve is a three-way valve, and the three interfaces of the three-way valve respectively correspond to the first connection port of the second four-way valve The third connection port; or The second four-way valve includes two shut-off valves, one end of which is formed as a first connecting port and one end of the other shut-off valve is formed as a third connecting port, and the other ends of the two shut-off valves are connected and formed together Is the second connection; or The second four-way valve includes a shut-off valve and a one-way valve, wherein one end of the one-way valve is formed as a first connecting port and one end of the shut-off valve is formed as a third connecting port, and the other end of the one-way valve and the shut-off valve The other ends are connected and collectively formed as a second connection port, and the one-way valve is electrically connected from the one end to the other end. The air conditioning system according to any one of claims 4 to 7, wherein the third four-way valve has first to fourth flow ports, and the first flow port is connected to the exhaust port. The second flow port is connected to the outdoor heat exchanger, the third flow port, the first connection port and the third interface are connected to each other, and the fourth flow port is used for heat exchange with the room Connected, the third four-way valve is configured to be switchable between a first communication state and a second communication state; In the first connected state, the first flow port is connected to the second flow port, the third flow port is connected to the fourth flow port, and in the second communication state, the first flow port is The fourth flow port is connected, and the second flow port is connected to the third flow port. The air conditioning system according to any one of claims 4 to 8, further comprising a gas-liquid separator, an inlet of the gas-liquid separator being connected to a third flow port of the third four-way valve, The outlet of the gas-liquid separator is respectively connected to the third interface of the first four-way valve and the first connection port of the second four-way valve. The air conditioning system according to claim 2 or 3, wherein in the independent compression mode of operation, the volume of the compression chamber in which the second cylinder portion participates in compression is V2', and the compression chamber in the first cylinder The volume is V1, which satisfies: V2'/V1 = 5%-30%. The air conditioning system according to claim 2 or 3, wherein in the variable volume operation mode, the volume of the compression chamber in which the second cylinder is all engaged in compression is V2, and the volume of the compression chamber in the first cylinder It is V1, which satisfies: V2/V1=30%-70%.

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