Compressor of air conditioning system and air conditioning system

Abstract

The present application relates to air conditioning equipment technical field, specifically provide a kind of compressor and air conditioning system of air conditioning system, to solve the problem of low energy efficiency of the variable capacity compressor of existing air conditioner under small load operating state.It is for this purpose, the compressor of the present application includes: shell and its internal cavity pump body, shell is equipped with total exhaust port communicated with cavity, pump body includes: upper cylinder, it is equipped with upper suction port and upper exhaust port on it, upper suction port is communicated with the evaporative pipeline of air conditioning system, and upper exhaust port is communicated with cavity;Lower cylinder, it is equipped with lower suction port and lower exhaust port on it, lower suction port is communicated with the evaporative pipeline;Pump body is further provided with direct discharge channel and intermediate channel, the gas inlet of direct discharge channel and intermediate channel is all communicated with lower exhaust port, the gas outlet of direct discharge channel is communicated with cavity, and the gas outlet of intermediate channel is communicated with upper suction port;Direct discharge channel or intermediate channel can be communicated to enable compressor to switch between single-stage mode and double-stage mode.

Description

Technical Field

[0001] This invention relates to the field of air conditioning equipment technology, specifically providing a compressor and an air conditioning system for an air conditioning system. Background Technology

[0002] Air conditioning systems often employ inverter technology to regulate load demand. When the load is too low, the compressor operates at a low frequency, reducing both the compressor's volumetric efficiency and the motor's efficiency. This results in low-frequency energy efficiency for the compressor, impacting the overall system performance. Furthermore, in hot summers and cold winters, as well as in frigid northern regions, there are also issues with poor heating performance at low temperatures, slow cooling at high temperatures, and low energy efficiency.

[0003] To address this, existing variable frequency compressors further achieve variable capacity by changing the number of cylinders that draw in refrigerant. This is achieved by adding a switching structure, allowing the compressor to switch between single-cylinder single-stage and dual-cylinder single-stage operating modes. This allows for the use of dual-cylinder single-stage high-displacement mode under heavy loads and single-cylinder single-stage low-displacement mode under light loads.

[0004] However, existing variable capacity compressors still suffer from low energy efficiency under low load conditions.

[0005] Therefore, a new technical solution is needed in this field to solve the above problems. Summary of the Invention

[0006] The present invention aims to solve the above-mentioned technical problem, namely, that existing variable capacity compressors have low energy efficiency under low load operation.

[0007] In a first aspect, the present invention provides a compressor for an air conditioning system, the compressor comprising a housing and a pump body, the pump body being installed within a cavity of the housing, a main exhaust port being provided at the top of the housing, the main exhaust port being connected to the condenser pipe of the air conditioning system, the pump body comprising: an upper cylinder, the interior of which forms an upper compression chamber, the upper cylinder having an upper intake port and an upper exhaust port, the upper intake port being connected to the evaporator pipe of the air conditioning system, and the upper exhaust port being connected to the cavity; and a lower cylinder, the interior of which forms a lower compression chamber, the lower cylinder having a lower intake port and a lower exhaust port, the lower intake port being connected to the cavity; and a lower cylinder, the interior of which forms a lower compression chamber, the lower cylinder having a lower intake port and a lower exhaust port. The air inlet is connected to the evaporation pipeline; the pump body is also provided with a direct discharge channel and an intermediate channel. The air inlet of the direct discharge channel and the air inlet of the intermediate channel are both connected to the lower exhaust port. The air outlet of the direct discharge channel is connected to the cavity, and the air outlet of the intermediate channel is connected to the upper suction port. A first valve assembly is provided on the direct discharge channel, and a second valve assembly is provided on the intermediate channel. Opening the first valve assembly or the second valve assembly can control the flow of gas in the lower compression chamber to the cavity or the upper suction port, so as to realize the switching of the compressor between the dual-cylinder single-stage compression mode and the dual-cylinder dual-stage compression mode.

[0008] In the preferred embodiment of the compressor described above, the first valve assembly is configured as a first one-way pneumatic valve, which can open in the direction of exhaust under the action of air pressure.

[0009] In the preferred embodiment of the compressor described above, the second valve assembly is configured as a solenoid three-way valve. The first inlet of the solenoid three-way valve is connected to the outlet of the intermediate channel, the second inlet of the solenoid three-way valve is connected to the evaporator pipe, and the outlet of the solenoid three-way valve is connected to the upper suction port. The outlet of the solenoid three-way valve can selectively connect to either the first inlet or the second inlet.

[0010] In the preferred embodiment of the compressor described above, the compressor further includes an upper air supply channel and a lower air supply channel, and the air conditioning system further includes an air supply pipeline. The air inlet of the upper air supply channel and the air inlet of the lower air supply channel are both connected to the air supply pipeline. The air outlet of the upper air supply channel is connected to the upper compression chamber, and the air outlet of the lower air supply channel is connected to the lower compression chamber.

[0011] In the preferred embodiment of the compressor described above, the compressor further includes a partition plate disposed between the upper cylinder and the lower cylinder to isolate the upper compression chamber from the lower compression chamber, and both the upper air supply channel and the lower air supply channel are disposed within the partition plate.

[0012] In the preferred embodiment of the compressor described above, a main air supply channel is further provided inside the partition. The air inlet of the main air supply channel is connected to the air supply pipeline, and the air outlet of the main air supply channel is connected to the air inlets of the upper air supply channel and the lower air supply channel. The main air supply channel is arranged radially along the partition, and the upper air supply channel and the lower air supply channel are both arranged axially along the partition.

[0013] In the preferred embodiment of the compressor described above, the compressor further includes a second one-way pneumatic valve, a third one-way pneumatic valve, a fourth one-way pneumatic valve, and a fifth one-way pneumatic valve. The second one-way pneumatic valve is located at the upper exhaust port, the third one-way pneumatic valve is located at the lower exhaust port, the fourth one-way pneumatic valve is located in the upper air supply channel, and the fifth one-way pneumatic valve is located in the lower air supply channel.

[0014] In the preferred embodiment of the above-mentioned compressor, the compressor further includes an upper muffler, an upper muffler cavity is formed within the upper muffler, the air inlet of the upper muffler cavity is connected to the air outlet of the straight exhaust channel and the upper exhaust port, and the air outlet of the upper muffler cavity is connected to the cavity; and / or the compressor further includes a lower muffler, a lower muffler cavity is formed within the lower muffler, the air inlet of the lower muffler cavity is connected to the lower exhaust port, and the air outlet of the lower muffler cavity is connected to the air inlet of the straight exhaust channel and the intermediate channel.

[0015] In the preferred embodiment of the compressor described above, the direct discharge channel is disposed through the lower cylinder, the partition, and the upper cylinder, and the first valve assembly is installed between the lower cylinder and the partition.

[0016] In a second aspect, the present invention provides an air conditioning system comprising the compressor described above.

[0017] When adopting the above technical solution, the compressor of the present invention includes a housing and a pump body. The pump body is installed in the cavity of the housing, and a main exhaust port is provided at the top of the housing. The main exhaust port connects the cavity to the condenser pipe of the air conditioning system. The pump body includes: an upper cylinder, the interior of which forms an upper compression chamber, and an upper suction port and an upper exhaust port are provided on the upper cylinder. The upper suction port is connected to the evaporator pipe of the air conditioning system, and the upper exhaust port is connected to the cavity; and a lower cylinder, the interior of which forms a lower compression chamber, and a lower suction port and a lower exhaust port are provided on the lower cylinder. The outlet is connected to the evaporator pipe; the pump body is also equipped with a direct exhaust channel and an intermediate channel. The air inlet of the direct exhaust channel and the air inlet of the intermediate channel are both connected to the lower exhaust port. The air outlet of the direct exhaust channel is connected to the cavity, and the air outlet of the intermediate channel is connected to the upper suction port. A first valve assembly is installed on the direct exhaust channel, and a second valve assembly is installed on the intermediate channel. Opening the first valve assembly or the second valve assembly can control the flow of gas in the lower compression chamber to the cavity or the upper suction port, so as to realize the switching of the compressor between the dual-cylinder single-stage compression mode and the dual-cylinder dual-stage compression mode. This configuration allows the compressor to select the appropriate operating mode under different air conditioning load conditions. Specifically, it selectively opens one of the two valve assemblies to control the exhaust path of the lower compression chamber. When the air conditioner is under low load, the first valve assembly is closed, and the outlet of the middle channel connects to the upper intake port, allowing the gas to undergo two compressions sequentially through the lower and upper compression chambers, achieving a dual-cylinder, two-stage, low-displacement mode. Conversely, when the air conditioner is under high load, the first valve assembly opens, keeping the direct exhaust channel connected, while the upper intake port connects to the evaporator pipe of the air conditioning system. This allows the upper and lower compression chambers to independently intake, compress, and exhaust air, achieving a dual-cylinder, single-stage, high-displacement mode. This reduces energy consumption under low load conditions and improves overall energy efficiency.

[0018] Furthermore, the first valve assembly of the present invention is configured as a first one-way pneumatic valve, which can open in the direction of exhaust under the action of air pressure. With this configuration, on the one hand, the automatic opening and closing of the first valve assembly can be achieved through the pressure difference on both sides, forming a linkage with the two modes of the air conditioning system; on the other hand, it can prevent gas backflow; and furthermore, it makes the switching between the two modes more stable and reliable.

[0019] Furthermore, the second valve assembly of the present invention is configured as an electromagnetic three-way valve. The first air inlet of the electromagnetic three-way valve is connected to the air outlet of the intermediate channel, the second air inlet of the electromagnetic three-way valve is connected to the evaporation pipe, and the air outlet of the electromagnetic three-way valve is connected to the upper suction port. The air outlet of the electromagnetic three-way valve can selectively connect to either the first air inlet or the second air inlet. By controlling the air outlet of the electromagnetic three-way valve to selectively connect to either the first air inlet or the second air inlet, the air pressure below the first one-way pneumatic valve can be controlled, thereby determining whether the gas discharged from the lower compression chamber can open the first one-way pneumatic valve to selectively enter the direct discharge channel or the intermediate channel, thus realizing the switching between the two compression modes.

[0020] Furthermore, the compressor of the present invention also includes an upper gas supply channel and a lower gas supply channel, and the air conditioning system also includes a gas supply pipeline. The inlet of the upper gas supply channel and the inlet of the lower gas supply channel are both connected to the gas supply pipeline. The outlet of the upper gas supply channel is connected to the upper compression chamber, and the outlet of the lower gas supply channel is connected to the lower compression chamber. With this configuration, in the low-load dual-cylinder dual-stage small-displacement mode, the gas supply of the low-pressure stage and the high-pressure stage can be superimposed, which greatly improves the gas supply volume, increases the enthalpy difference on the evaporation side, and enables the low-pressure stage to achieve continuous gas supply throughout the entire process, effectively reducing the compression work of the low-pressure stage, thereby effectively improving the overall energy efficiency of the compressor and heat pump system under low load. In the high-load dual-cylinder single-stage large-displacement mode, the single-stage gas supply of the lower cylinder and the upper cylinder effectively improves the gas supply volume, increases the enthalpy difference on the evaporation side, improves the performance under high load and low temperature high pressure ratio, and effectively reduces the exhaust temperature, thereby improving the operational reliability of the compressor and heat pump system under high load.

[0021] Furthermore, the compressor of the present invention also includes a partition plate disposed between the upper cylinder and the lower cylinder to isolate the upper compression chamber from the lower compression chamber. Both the upper and lower air supply channels are disposed within the partition plate. This arrangement allows the position and structure of the two air supply channels to be adapted to the overall structure of the pump body, ensuring stable air supply to the upper and lower compression chambers while also helping to reduce the machining difficulty of the pump body.

[0022] Furthermore, the partition of the present invention also includes a main air supply channel. The air inlet of the main air supply channel is connected to the air supply pipeline, and the air outlet of the main air supply channel is connected to the air inlets of the upper and lower air supply channels. The main air supply channel is arranged radially along the partition, while the upper and lower air supply channels are arranged axially along the partition. By extending the air supply channels radially and axially, the difficulty of drilling holes is reduced, and the installation of the internal one-way pneumatic valve is facilitated.

[0023] Furthermore, the compressor of the present invention also includes a second one-way pneumatic valve, a third one-way pneumatic valve, a fourth one-way pneumatic valve, and a fifth one-way pneumatic valve. The second one-way pneumatic valve is located at the upper exhaust port, the third one-way pneumatic valve is located at the lower exhaust port, the fourth one-way pneumatic valve is located in the upper air supply channel, and the fifth one-way pneumatic valve is located in the lower air supply channel. This arrangement enables automatic differential pressure control of the opening and closing of the upper exhaust port, lower exhaust port, upper air supply channel, and lower air supply channel; simultaneously, it achieves one-way connectivity to prevent gas backflow.

[0024] Furthermore, the compressor of the present invention also includes an upper muffler, which forms an upper muffler cavity. The air inlet of the upper muffler cavity is connected to the air outlet of the straight exhaust channel and the upper exhaust port, and the air outlet of the upper muffler cavity is connected to the cavity. And / or the compressor also includes a lower muffler, which forms a lower muffler cavity. The air inlet of the lower muffler cavity is connected to the lower exhaust port, and the air outlet of the lower muffler cavity is connected to the air inlet of the straight exhaust channel and the intermediate channel. With this arrangement, expansion-type silencing can be achieved by transferring and reducing the kinetic energy of the gas, thus providing a certain degree of noise reduction for both the upper and lower cylinder blocks.

[0025] Furthermore, the straight discharge channel of the present invention is configured to penetrate the lower cylinder body, the partition plate, and the upper cylinder body, and the first valve assembly is installed between the lower cylinder body and the partition plate. This configuration allows for compatibility with the overall structure of the pump body and makes efficient use of the space within the pump body.

[0026] Furthermore, the air conditioning system provided by the present invention, based on the above-mentioned compressor, includes the above-mentioned compressor and thus possesses the technical effects of the above-mentioned compressor. Compared with the air conditioning system before the improvement, the air conditioning system of the present invention can switch the operating state in a timely manner according to the load size, improve the overall energy efficiency of the air conditioning system under low load operating conditions, and make the operation of the air conditioning system more stable and reliable. Attached Figure Description

[0027] The preferred embodiments of the present invention are described below with reference to the accompanying drawings, in which:

[0028] Figure 1 This is a schematic diagram of the compressor structure of the air conditioning system of the present invention;

[0029] Figure 2 This is a structural schematic diagram of the air conditioning system of the present invention.

[0030] List of reference numerals in the attached diagram:

[0031] 1. Housing; 11. Cavity; 12. Main exhaust port; 2. Pump body; 21. Upper cylinder block; 211. Upper intake port; 212. Upper exhaust port; 22. Lower cylinder block; 221. Lower intake port; 222. Lower exhaust port; 23. Baffle; 231. Upper air intake passage; 232. Lower air intake passage; 233. Main air intake passage; 24. Upper muffler; 241. Upper muffler chamber; 25. Lower muffler; 251. Lower muffler chamber; 26. Straight exhaust passage; 27. Intermediate passage; 281. 1. One-way pneumatic valve; 282. Second one-way pneumatic valve; 283. Third one-way pneumatic valve; 284. Fourth one-way pneumatic valve; 285. Fifth one-way pneumatic valve; 286. Solenoid three-way valve; 31. Condensing line; 311. Condenser; 32. Evaporator line; 321. First electronic expansion valve; 322. Evaporator; 33. First evaporation branch; 34. Second evaporation branch; 35. Make-up gas line; 351. Second electronic expansion valve; 36. Liquid distributor; 37. Economic heat exchanger. Detailed Implementation

[0032] Preferred embodiments of the present invention will now be described with reference to the accompanying drawings. Those skilled in the art should understand that these embodiments are merely illustrative of the technical principles of the present invention and are not intended to limit the scope of protection of the present invention.

[0033] It should be noted that in the description of this invention, terms such as "inner," "outer," "upper," "lower," "top," and "bottom," which indicate direction or positional relationships, are based on the direction or positional relationships shown in the accompanying drawings. These are used merely for ease of description and do not indicate or imply that the device or element must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention. Furthermore, the terms "first," "second," "third," "fourth," and "fifth" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0034] Furthermore, it should be noted that, in the description of this invention, unless otherwise explicitly specified and limited, the terms "set up," "install," and "connect" should be interpreted broadly, and those skilled in the art can understand the specific meaning of the above terms in this invention according to the specific circumstances.

[0035] As pointed out in the background art, existing variable-capacity compressors suffer from low energy efficiency under low-load operation. This invention provides a compressor and air conditioning system for an air conditioning system. By incorporating a direct discharge channel, an intermediate channel, a first one-way pneumatic valve, and a solenoid three-way valve within the compressor, and controlling the solenoid three-way valve to alter the intake path of the upper compression chamber, the pressure difference across the first one-way pneumatic valve is controlled. This pressure difference controls the opening and closing of the first one-way pneumatic valve, allowing gas discharged from the lower compression chamber to selectively enter the upper compression chamber for secondary compression or be directly discharged into the circulation system. This enables the air conditioning system to switch between a dual-cylinder single-stage small-displacement mode and a dual-cylinder two-stage large-displacement mode.

[0036] Specifically, existing variable frequency compressors further achieve variable capacity by changing the number of cylinders that draw in refrigerant. By adding a switching mechanism, they can achieve two operating modes: single-cylinder single-stage and double-cylinder single-stage. This allows for the use of double-cylinder single-stage large displacement mode under heavy load and single-cylinder single-stage small displacement mode under light load.

[0037] Existing switching structures typically employ either a pin-based differential pressure switching structure or a magnet-based differential pressure switching structure. The pin-based differential pressure switching structure uses differential pressure to control the pin, locking or unlocking the slide to achieve switching between single-cylinder single-stage and dual-cylinder single-stage operating modes. The magnet-based differential pressure switching structure uses differential pressure to control whether the magnet attracts the slide to achieve switching between single-cylinder single-stage and dual-cylinder single-stage operating modes.

[0038] In low-load, single-cylinder, single-stage, small-displacement operation modes, the rollers in the unloading cylinder continue to run, and this movement is ineffective, increasing power consumption under low load and affecting the overall energy efficiency of the compressor and even the system. Simultaneously, the pin head is prone to wear against the vane locking groove, and the magnet easily attracts iron powder and other impurities, all of which affect the reliability of the switching structure, and consequently, the reliability of the compressor and even the air conditioning system.

[0039] Based on this, such as Figure 1 and Figure 2 As shown, the present invention provides a compressor for an air conditioning system and an air conditioning system, wherein the compressor includes a housing 1, a pump body 2 and a motor. The housing 1 forms a sealed cavity 11 inside. The pump body 2 is installed in the lower part of the cavity 11 and the motor is installed in the upper part of the cavity 11. A main exhaust port 12 is provided at the top of the housing 1, and the main exhaust port 12 connects the cavity 11 with the condenser pipe 31 of the air conditioning system.

[0040] Preferably, such as Figure 1 As shown, the pump body 2 includes, from top to bottom, an upper bearing, an upper silencer 24, an upper cylinder 21, a partition 23, a lower cylinder 22, a lower silencer 25, and a lower bearing. The motor is connected to the upper and lower rotors inside the upper and lower cylinders 22 through the bearings and the transmission shaft to transmit power and realize the compression of gas to do work.

[0041] The upper cylinder 21 has an upper compression chamber inside, which is used to compress the gas drawn in by the rotor. The upper cylinder 21 is provided with an upper intake port 211 and an upper exhaust port 212. The upper intake port 211 is connected to the evaporator pipe 32 of the air conditioning system for intake. The upper exhaust port 212 is connected to the cavity 11 of the housing 1 through the upper silencer 241 formed in the upper silencer 24, so that the compressed gas can pass through the upper silencer 241 and the cavity 11 in sequence and then be discharged into the condenser pipe 31 through the main exhaust port 12.

[0042] The lower cylinder 22 forms a lower compression chamber inside, and the rotor compresses the gas drawn in. The lower cylinder 22 is provided with a lower intake port 221 and a lower exhaust port 222. The lower intake port 221 is connected to the evaporator pipe 32 of the air conditioning system to draw in gas, and the lower exhaust port 222 is connected to the lower muffler 251 formed in the lower muffler 25, so that the exhaust gas enters the lower muffler 251.

[0043] The pump body 2 is also provided with a straight discharge channel 26 and an intermediate channel 27. The air inlets of the straight discharge channel 26 and the intermediate channel 27 are connected to the lower silencer 251, the air outlet of the straight discharge channel 26 is connected to the upper silencer 241, and the air outlet of the intermediate channel 27 is connected to the upper suction port 211.

[0044] A first valve assembly is provided on the straight channel 26, and a second valve assembly is provided on the intermediate channel 27. By opening the first valve assembly or the second valve assembly, the compressed gas in the lower silencer 251 can be controlled to flow to the upper silencer 241 or the upper compression chamber.

[0045] It should be noted that in practical applications, both the first valve assembly and the second valve assembly can be configured as various control valves, such as solenoid valves, pneumatic valves, etc., as long as they can control the opening and closing of the direct discharge channel 26 and the intermediate channel 27. Such flexible adjustments and changes do not deviate from the principles and scope of the present invention and should be limited to the protection scope of the present invention.

[0046] Preferably, the first valve assembly is configured as a first one-way pneumatic valve 281, which can open when the pressure at its inlet end is greater than the pressure at its outlet end, and close when the pressure at its inlet end is not greater than the pressure at its outlet end, while preventing gas from flowing back from the outlet end to the inlet end.

[0047] The second valve assembly is configured as a solenoid three-way valve 286, which connects the first air inlet of the solenoid three-way valve 286 to the air outlet of the intermediate channel 27, the second air inlet of the solenoid three-way valve 286 to the evaporation pipe 32, and the air outlet of the solenoid three-way valve 286 to the upper suction port 211. Furthermore, the air outlet can selectively connect to the first air inlet or the second air inlet under the control of an electrical signal.

[0048] A second one-way pneumatic valve 282 and a third one-way pneumatic valve 283 are respectively installed at the upper exhaust port 212 and the lower exhaust port 222. The opening and closing principle of the two valves is the same as that of the first one-way pneumatic valve 281, which will not be described in detail here.

[0049] Preferably, such as Figure 1 As shown, the pump body 2 also includes a partition 23 disposed between the upper cylinder 21 and the lower cylinder 22, which can isolate the upper compression chamber from the lower compression chamber. The partition 23 is also provided with a main air supply channel 233, an upper air supply channel 231 and a lower air supply channel 232. The air inlet of the main air supply channel 233 is connected to the air supply pipe 35 of the air conditioning system, and the air outlet of the main air supply channel 233 is connected to the air inlets of the upper air supply channel 231 and the lower air supply channel 232. The air outlet of the upper air supply channel 231 is connected to the upper compression chamber, and the air outlet of the lower air supply channel 232 is connected to the lower compression chamber. The main air supply channel 233 is disposed radially in the middle of the partition 23, and the upper air supply channel 231 and the lower air supply channel 232 are disposed axially in the upper and lower parts of the partition 23, respectively.

[0050] This configuration, in the low-load, dual-cylinder, dual-stage, small-displacement mode, achieves superimposed gas replenishment between the low-pressure and high-pressure stages, significantly increasing the gas replenishment volume, expanding the enthalpy difference on the evaporator side, and enabling continuous gas replenishment to the low-pressure stage throughout the entire process. This effectively reduces the compression work of the low-pressure stage, thereby significantly improving the overall energy efficiency of the compressor and heat pump system under low load. In the high-load, dual-cylinder, single-stage, large-displacement mode, single-stage gas replenishment through the lower and upper cylinders effectively increases the gas replenishment volume and expands the enthalpy difference on the evaporator side, improving performance under high load and low-temperature, high-pressure ratio conditions. It also effectively reduces the exhaust temperature, improving the operational reliability of the compressor and heat pump system under high load. Simultaneously, the position and structure of the gas replenishment channel are compatible with the overall structure of the pump body 2, ensuring stable gas replenishment to the upper and lower compression chambers while also helping to reduce the machining difficulty of the pump body 2.

[0051] Preferably, the straight discharge channel 26 is disposed inside the pump body 2, and the intermediate channel 27 is disposed outside the pump body 2. The straight discharge channel 26 passes through the lower bearing, the lower cylinder 22, the partition 23, the upper cylinder 21 and the upper bearing from bottom to top. The first one-way pneumatic valve 281 can be disposed on the upper end face of any part of the upper bearing, the upper cylinder 21, the partition 23 or the lower bearing. In this case, it is preferably disposed between the upper end face of the lower cylinder and the partition 23.

[0052] Accordingly, to adapt to the specific structure of the compressor, the present invention also provides an air conditioning system, such as... Figure 2As shown, the air conditioning system includes the compressor described above, as well as a condenser pipe 31, an evaporator pipe 32, a first evaporator branch 33, a second evaporator branch 34, and a make-up air pipe 35 connected thereto. The inlet end of the condenser pipe 31 is connected to the compressor's main exhaust port 12. The first outlet end of the condenser pipe 31 is connected to the inlet end of the evaporator pipe 32. The first outlet end of the evaporator pipe 32 is connected to the lower suction port 221 through the first evaporator branch 33. The second outlet end of the evaporator pipe 32 is connected to the second air inlet of the solenoid three-way valve 286 through the second evaporator branch 34. The second outlet end of the condenser pipe 31 is connected to the inlet end of the make-up air pipe 35. The outlet end of the make-up air pipe 35 is connected to the air inlet of the main make-up air channel 233.

[0053] A condenser 311 is installed on the condensing pipe 31, and a first electronic expansion valve 321 and an evaporator 322 are installed on the evaporating pipe 32. A liquid separator 36 is also installed between the evaporating pipe 32 and the first evaporating branch 33 and the second evaporating branch 34 to achieve gas-liquid separation. A second electronic expansion valve 351 is installed on the gas supply pipe 35. In addition, the gas supply pipe 35 and the condensing pipe 31 also pass through an economic heat exchanger 37 for heat exchange.

[0054] The following is combined Figure 1 and Figure 2 A detailed explanation of the compressor and the switching principle between the two modes is provided:

[0055] When the load on the air conditioning system is low, the controller will connect the first inlet and outlet of the solenoid three-way valve 286 and disconnect the second inlet and outlet. At this time, only the first evaporation branch 33 supplies gas to the lower compression chamber, and the second evaporation branch 34 does not supply gas to the upper compression chamber. That is, after the low temperature and low pressure gas flows out from the distributor 36, it enters the lower compression chamber through the first evaporation branch 33 and the lower suction port 221 for compression. Since the intermediate channel 27 is in a closed state, the compressed medium temperature and medium pressure gas is discharged from the lower exhaust port 222 and enters the intermediate channel 27 through the lower silencer 251. Then it is sucked into the upper compression chamber for secondary compression. The high temperature and high pressure gas after secondary compression enters the upper silencer 241 through the upper exhaust port 212 and enters the condenser pipe 31 for circulation in sequence through the cavity 11 and the main exhaust port 12.

[0056] Since the two ends of the direct exhaust channel 26 are connected to the lower silencer 251 and the upper silencer 241 respectively, the lower silencer 251 contains medium-temperature and medium-pressure gas, while the upper silencer 241 contains high-temperature and high-pressure gas. This causes the inlet pressure of the first one-way pneumatic valve 281 to be less than the outlet pressure, thereby keeping the first one-way pneumatic valve 281 closed and maintaining the air conditioning system in a dual-cylinder, dual-stage, small-displacement mode.

[0057] When the load on the air conditioning system is detected to be large, the controller will connect the second air inlet and the air outlet of the electromagnetic three-way valve 286, and disconnect the first air inlet and the air outlet. At this time, the first evaporation branch 33 and the second evaporation branch 34 supply air to the lower compression chamber and the upper compression chamber respectively. The low temperature and low pressure gas flows out from the distributor 36 and is divided into two paths. The first path enters the lower compression chamber through the first evaporation branch 33 and the lower suction port 221 for compression. Since the intermediate channel 27 is in a closed state, the high temperature and high pressure gas after compression is discharged from the lower exhaust port 222 and passes through the lower silencer 251. It will form a large pressure at the inlet end of the first one-way pneumatic valve 281 and push the first one-way pneumatic valve 281 open, making the straight discharge channel 26 open. At this time, the medium temperature and medium pressure gas will enter the upper silencer 241 through the straight discharge channel 26.

[0058] The second path passes through the second evaporation branch 34 and the upper intake port 211 to enter the upper compression chamber for compression. The compressed high-temperature and high-pressure gas also enters the upper silencer chamber 241 through the upper exhaust port 212, so that the high-temperature and high-pressure gas discharged from the upper and lower compression chambers are discharged together through the cavity 11 and the main exhaust port 12 and then discharged into the condenser pipe 31 for circulation, realizing the dual-cylinder single-stage large displacement mode of the air conditioning system.

[0059] At the same time, the replenishment of qi and increase of enthalpy are always accompanied by two modes of operation, specifically, such as Figure 1 and Figure 2 As shown, a portion of the refrigerant diverted from the condenser pipe 31 enters the make-up gas pipe 35. After being throttled by the second electronic expansion valve 351, it becomes a medium-temperature, medium-pressure gas-liquid two-phase refrigerant. Then, it exchanges heat with the high-temperature, high-pressure refrigerant in the condenser pipe 31 in the economic heat exchanger 37 and becomes a medium-temperature, medium-pressure saturated gas. The medium-temperature, medium-pressure saturated gas enters the main make-up gas channel 233 and is diverted by the upper make-up gas channel 231 and the lower make-up gas channel 232, and then enters the upper compression chamber and the lower compression chamber respectively to complete the make-up gas process.

[0060] Preferably, a fourth one-way pneumatic valve 284 and a fifth one-way pneumatic valve 285 are respectively provided in the upper air supply channel 231 and the lower air supply channel 232. Similarly, the fourth one-way pneumatic valve 284 and the fifth one-way pneumatic valve 285 are both configured such that when the pressure at the air inlet end is greater than the pressure at the air outlet end, the pressure difference generated on both sides will open the one-way valve to achieve air supply.

[0061] When the air conditioning system is in dual-cylinder, dual-stage, small-displacement mode, the lower cylinder 22 is a low-pressure cylinder forming the low-pressure stage, and the upper cylinder 21 is a high-pressure cylinder forming the high-pressure stage, achieving dual-cylinder, dual-stage compression. Simultaneously, when medium-temperature, medium-pressure saturated gas is supplied to the lower and upper compression chambers from the gas supply line 35, the combined gas supply effect of the low-pressure and high-pressure stages is achieved, significantly increasing the gas supply volume.

[0062] It should be noted that the pressure of the medium-temperature and medium-pressure saturated gas supplied from the lower intake port 221 is greater than or equal to the pressure of the medium-temperature and medium-pressure gas discharged from the lower exhaust port 222. This achieves continuous gas supply throughout the low-pressure stage, greatly increases the gas supply volume, increases the enthalpy difference on the evaporator side, reduces the compression work of the low-pressure stage, and improves the compressor performance and overall energy efficiency of the heat pump system in the dual-cylinder, dual-stage, small-displacement mode.

[0063] When the air conditioning system is in dual-cylinder, single-stage, large-displacement mode, the compression stages formed by the lower cylinder 22 and the upper cylinder 21 are both single-stage and not connected to each other, achieving dual-cylinder, single-stage compression. Simultaneously, when medium-temperature, medium-pressure saturated gas is supplied to the lower and upper compression chambers from the gas supply line 35, the effect of single-stage gas supply to the lower cylinder 22 and upper cylinder 21 is achieved. This effectively increases the gas supply volume, increases the enthalpy difference on the evaporator side, improves performance under high load and low-temperature, high-pressure ratios, and effectively reduces the exhaust temperature, thereby improving the operational reliability of the compressor and heat pump system.

[0064] Furthermore, the air conditioning system provided by the present invention, based on the above-mentioned compressor, includes the above-mentioned compressor and thus possesses the technical effects of the above-mentioned compressor. Compared with the air conditioning system before the improvement, the air conditioning system of the present invention can switch the operating state in a timely manner according to the load size, improve the overall energy efficiency of the air conditioning system under low load operating conditions, and make the operation of the air conditioning system more stable and reliable.

[0065] The technical solution of the present invention has been described above with reference to the preferred embodiments shown in the accompanying drawings. However, it will be readily understood by those skilled in the art that the scope of protection of the present invention is obviously not limited to these specific embodiments. Without departing from the principles of the present invention, those skilled in the art can make equivalent changes or substitutions to the relevant technical features, and the technical solutions after such changes or substitutions will all fall within the scope of protection of the present invention.

Claims

1. A compressor for an air conditioning system, characterized in that, The compressor includes a housing (1) and a pump body (2). The pump body (2) is installed in the cavity (11) of the housing (1). A main exhaust port (12) is provided on the top of the housing (1). The main exhaust port (12) connects the cavity (11) to the condenser pipe (31) of the air conditioning system. The pump body (2) includes: The upper cylinder (21) has an upper compression chamber inside. The upper cylinder (21) is provided with an upper intake port (211) and an upper exhaust port (212). The upper intake port (211) is connected to the evaporator pipe (32) of the air conditioning system, and the upper exhaust port (212) is connected to the cavity (11). The lower cylinder (22) has a lower compression chamber inside. The lower cylinder (22) is provided with a lower intake port (221) and a lower exhaust port (222). The lower intake port (221) is connected to the evaporator pipe (32). The pump body (2) is also provided with a straight discharge channel (26) and an intermediate channel (27). The air inlet of the straight discharge channel (26) and the air inlet of the intermediate channel (27) are both connected to the lower exhaust port (222). The air outlet of the straight discharge channel (26) is connected to the cavity (11). The air outlet of the intermediate channel (27) is connected to the upper suction port (211). A first valve assembly is provided on the straight discharge channel (26), and a second valve assembly is provided on the intermediate channel (27). Opening the first valve assembly or the second valve assembly can control the flow of gas in the lower compression chamber to the cavity (11) or the upper intake port (211), so as to realize the compressor switching between the dual-cylinder single-stage compression mode and the dual-cylinder dual-stage compression mode.

2. The compressor according to claim 1, characterized in that, The first valve assembly is configured as a first one-way pneumatic valve (281), which can be opened in the direction of exhaust under the action of air pressure.

3. The compressor according to claim 1, characterized in that, The second valve assembly is configured as a solenoid three-way valve (286). The first air inlet of the solenoid three-way valve (286) is connected to the air outlet of the intermediate channel (27), the second air inlet of the solenoid three-way valve (286) is connected to the evaporation pipe (32), the air outlet of the solenoid three-way valve (286) is connected to the upper suction port (211), and the air outlet of the solenoid three-way valve (286) can selectively connect to the first air inlet or the second air inlet.

4. The compressor according to claim 1, characterized in that, The compressor also includes an upper air supply channel (231) and a lower air supply channel (232). The air conditioning system also includes an air supply pipeline (35). The air inlet of the upper air supply channel (231) and the air inlet of the lower air supply channel (232) are both connected to the air supply pipeline (35). The air outlet of the upper air supply channel (231) is connected to the upper compression chamber, and the air outlet of the lower air supply channel (232) is connected to the lower compression chamber.

5. The compressor according to claim 4, characterized in that, The compressor also includes a partition (23), which is disposed between the upper cylinder (21) and the lower cylinder (22) to isolate the upper compression chamber from the lower compression chamber. The upper air supply channel (231) and the lower air supply channel (232) are both disposed within the partition (23).

6. The compressor according to claim 5, characterized in that, The partition (23) is also provided with a main air supply channel (233). The air inlet of the main air supply channel (233) is connected to the air supply pipeline (35). The air outlet of the main air supply channel (233) is connected to the air inlets of the upper air supply channel (231) and the lower air supply channel (232). The main air supply channel (233) is arranged radially along the partition (23), and the upper air supply channel (231) and the lower air supply channel (232) are both arranged axially along the partition (23).

7. The compressor according to claim 4, characterized in that, The compressor also includes a second one-way pneumatic valve (282), a third one-way pneumatic valve (283), a fourth one-way pneumatic valve (284), and a fifth one-way pneumatic valve (285). The second one-way pneumatic valve (282) is located at the upper exhaust port (212), the third one-way pneumatic valve (283) is located at the lower exhaust port (222), the fourth one-way pneumatic valve (284) is located in the upper air supply channel (231), and the fifth one-way pneumatic valve (285) is located in the lower air supply channel (232).

8. The compressor according to claim 1, characterized in that, The compressor further includes an upper silencer (24), which forms an upper silencer cavity (241). The air inlet of the upper silencer cavity (241) is connected to the air outlet of the straight exhaust channel (26) and the upper exhaust port (212). The air outlet of the upper silencer cavity (241) is connected to the cavity (11); and / or The compressor also includes a lower muffler (25), which forms a lower muffler cavity (251). The air inlet of the lower muffler cavity (251) is connected to the lower exhaust port (222), and the air outlet of the lower muffler cavity (251) is connected to the air inlet of the straight exhaust channel (26) and the intermediate channel (27).

9. The compressor according to claim 5, characterized in that, The straight discharge channel (26) is disposed through the lower cylinder (22), the partition (23) and the upper cylinder (21), and the first valve assembly is installed between the lower cylinder (22) and the partition (23).

10. An air conditioning system, characterized in that, The air conditioning system includes the compressor according to any one of claims 1 to 9.

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