Pump body assembly, compressor, dual-temperature air conditioning system

Abstract

The application provides a pump body assembly, a compressor and a double-temperature air conditioning system, wherein the pump body assembly comprises a high-pressure compression part and a low-pressure compression part, the high-pressure compression part comprises a first cylinder and a first sliding vane, the low-pressure compression part comprises a second cylinder and a second sliding vane, the high-pressure compression part is provided with a first air supplement port, the low-pressure compression part is provided with a second air supplement port, the first sliding vane and the second sliding vane are coincident, a first center included angle β between a center line of air supplement of the first air supplement port and a center line of symmetry of the first sliding vane is based on a center of the first cylinder, a second center included angle α between a center line of air supplement of the second air supplement port and a center line of symmetry of the second sliding vane is based on a center of the second cylinder, and α>β. According to the application, different requirements of the high-pressure compression part and the low-pressure compression part in terms of suction pressure are met, the system energy efficiency is effectively improved, the structure is more compact, the miniaturization design of the compressor is facilitated, and the volumetric efficiency of the compressor is improved.

Description

Technical Field

[0001] This invention belongs to the field of air conditioning technology, specifically relating to a pump assembly, a compressor, and a dual-temperature air conditioning system. Background Technology

[0002] As a device for regulating environmental comfort, air conditioning systems have evolved from simple temperature control to more diverse functions, catering to people's ever-increasing demands for comfortable living environments. Currently, the main dehumidification method in air conditioning systems is cooling dehumidification, which involves lowering the surface temperature of the indoor heat exchanger below the air dew point. When indoor air flows over the heat exchanger surface, water vapor in the air condenses, removing moisture. This method is suitable for high-temperature environments, simultaneously dehumidifying and cooling the room. However, during the "plum rain season" in the Yangtze River basin or the "return to spring" period in South China, when temperatures are not high but relative humidity is, conventional household inverter air conditioners experience a gradual decrease in indoor return air temperature and dew point during cooling dehumidification in transitional seasons. The indoor relative humidity, after reaching a certain level, stops decreasing and may even increase, resulting in a cool but not dry indoor environment. Furthermore, the decrease in evaporation temperature and return air dew point significantly reduces the dehumidification capacity per unit of energy consumption for the air conditioner. Therefore, during humid transitional weather, conventional household inverter air conditioners cannot meet the comfort requirements for dehumidification and are usually idle.

[0003] A related technology proposes a three-cylinder, dual-temperature parallel air conditioning system. This system achieves dual-temperature cascade heat exchange in cooling mode. The parallel cylinders effectively reduce the dryness of the evaporator inlet, increasing the cooling capacity of the indoor evaporator and improving the cooling energy efficiency ratio. The system also features reheat dehumidification, enabling dehumidification without temperature drop during transitional seasons. However, this solution uses a three-cylinder compressor with a separate injection cylinder, resulting in high costs. At lower displacements, the smaller cylinder (injection cylinder) is limited by the crankshaft diameter, preventing miniaturization and optimal cylinder parameters, leading to low volumetric efficiency, significant mechanical damage, and poor system performance. Furthermore, in a dual-evaporation temperature (i.e., dual-temperature) air conditioning system, the suction pressures of the two cylinders are different. Existing conventional dual-cylinder quasi-two-stage compressors have identical angles between the injection ports and corresponding vanes for both cylinders, which is clearly unsuitable for the requirements of a dual-temperature air conditioning system. Therefore, it is necessary to optimize the aforementioned angles of the two cylinders. This invention addresses these issues. Summary of the Invention

[0004] Therefore, the present invention provides a pump body assembly, a compressor, and a dual-temperature air conditioning system, which can overcome the shortcomings of related technologies, such as the high manufacturing cost of the compressor due to the separate setting of the air injection cylinder, and the inability to miniaturize the compressor due to the limitation of the air injection cylinder on the crankshaft diameter.

[0005] To address the aforementioned problems, the present invention provides a pump body assembly, comprising a high-pressure compression section and a low-pressure compression section. The high-pressure compression section includes a first cylinder and a corresponding first sliding vane, while the low-pressure compression section includes a second cylinder and a corresponding second sliding vane. The high-pressure compression section has a first air inlet, and the low-pressure compression section has a second air inlet. Projected onto a radial plane of the pump body assembly, the first and second sliding vanes coincide. A first central angle β, based on the center of the first air inlet and the center of symmetry of the first sliding vane, exists between the air inlet centerline and the center of symmetry of the first sliding vane. Similarly, a second central angle α, where α > β, exists between the air inlet centerline and the center of symmetry of the second sliding vane.

[0006] In some implementations, 56°≤β≤238°; and / or, 63°≤α≤273°.

[0007] In some embodiments, when the pump assembly is applied to a dual-temperature air conditioning system and the dual-temperature air conditioning system is operating in cooling mode, the first cylinder is connected in series with the indoor windward heat exchanger, the second cylinder is connected in series with the indoor leeward heat exchanger, the volume ratio of the first cylinder to the second cylinder is a, the load ratio of the indoor windward heat exchanger to the indoor leeward heat exchanger is b, and 0.7≤a / b≤1.1.

[0008] In some implementations, 0.9 ≤ a ≤ 1.3; and / or, 0.72 ≤ b ≤ 1.04; and / or, a / b = 0.8.

[0009] In some embodiments, a partition plate is sandwiched between the first cylinder and the second cylinder, and the first air inlet and the second air inlet are respectively disposed on two opposite end faces of the partition plate. The partition plate is provided with an air inlet channel communicating with the first air inlet and the second air inlet, and the air inlet channel has a main air inlet connected to an external air inlet pipeline.

[0010] The present invention also provides a pump body assembly, including a high-pressure compression section and a low-pressure compression section, wherein the high-pressure compression section includes a first cylinder and a first vane correspondingly disposed thereto, and the low-pressure compression section includes a second cylinder and a second vane correspondingly disposed thereto. One of the high-pressure compression section and the low-pressure compression section has an air inlet, which is projected onto a radial plane of the pump body assembly. The first vane and the second vane coincide. When the high-pressure compression section has the air inlet, the air inlet center line and the symmetry center line of the first vane have a first central angle β based on the center of the first cylinder, where 56°≤β≤144°; or, when the low-pressure compression section has the air inlet, the air inlet center line and the symmetry center line of the second vane have a second central angle α based on the center of the second cylinder, where 63°≤α≤166°.

[0011] In some embodiments, a partition plate is sandwiched between the first cylinder and the second cylinder, and the air inlet is disposed on one end face of the partition plate. The partition plate has an air inlet channel communicating with the air inlet, and the air inlet channel has a main air inlet connected to an external air inlet pipeline.

[0012] The present invention also provides a compressor including the pump body assembly described above.

[0013] The present invention also provides a dual-temperature air conditioning system, including a compressor, wherein the compressor is the compressor described above.

[0014] In some embodiments, the dual-temperature air conditioning system further includes a first four-way reversing valve, a second four-way reversing valve, an indoor windward heat exchanger, an indoor leeward heat exchanger, an outdoor heat exchanger, and a first throttling element. The first and second four-way reversing valves each have a D port that is connected to the exhaust port of the compressor. The first four-way reversing valve has a C port that is connected to the end of the outdoor heat exchanger away from the first throttling element. The first four-way reversing valve's E and S ports, along with the second four-way reversing valve's C port, are connected to the end of the indoor windward heat exchanger away from the first throttling element and to the first intake port of the high-pressure compressor section. A one-way valve is provided on the branch connecting the second four-way reversing valve's C port, allowing refrigerant to flow into the C port while simultaneously blocking it in the reverse direction. The second four-way reversing valve's S port is connected to the second intake port of the low-pressure compressor section. The second four-way reversing valve's E port is connected to the end of the indoor leeward heat exchanger away from the first throttling element.

[0015] This invention provides a pump assembly, a compressor, and a dual-temperature air conditioning system. On one hand, by misaligning the first and second air inlets of the high-pressure and low-pressure compression sections on the axial projection of the pump assembly, it adapts to the different suction pressure requirements of the high-pressure and low-pressure compression sections, thereby effectively improving the system's energy efficiency (SEER). On the other hand, by providing corresponding air inlets for the high-pressure and low-pressure compression sections respectively, without a separate air inlet cylinder (i.e., the smallest diameter cylinder in a three-cylinder compressor), the manufacturing cost of the compressor is reduced. Furthermore, when the compressor displacement is small, there is no need to consider the relationship between the air inlet cylinder and the crankshaft diameter, allowing for optimized design of the parameters of the first and second cylinders. The more compact structure facilitates the miniaturization of the compressor and improves its volumetric efficiency. Attached Figure Description

[0016] Figure 1 This is a simplified schematic diagram of the pump body assembly projected along its axial direction according to an embodiment of the present invention.

[0017] Figure 2 This is a schematic diagram (simplified schematic diagram) of the internal structure of a compressor according to another embodiment of the present invention;

[0018] Figure 3 for Figure 2 A schematic diagram of the structure of the partition plate in the middle;

[0019] Figure 4 This is a schematic diagram (simplified schematic diagram) of the internal structure of a compressor according to another embodiment of the present invention;

[0020] Figure 5 for Figure 4 A schematic diagram of the structure of the partition plate in the middle;

[0021] Figure 6 This is a schematic diagram (including a diagram of refrigerant flow direction) of a dual-temperature air conditioning system in cooling mode according to an embodiment of the present invention.

[0022] Figure 7 This is a schematic diagram (including a diagram of refrigerant flow direction) of a dual-temperature air conditioning system in heating mode according to an embodiment of the present invention.

[0023] Figure 8 This is a schematic diagram (including a diagram of refrigerant flow direction) of a dual-temperature air conditioning system in dehumidification and reheat mode according to an embodiment of the present invention.

[0024] Figure 9 for Figure 1 The diagram shows the correlation between α / β and the energy efficiency improvement compared to a single-stage system in the pump assembly.

[0025] Figure 10This is a schematic diagram of the correlation curve between the volume ratio 'a' and the proportion of the relative optimal value;

[0026] Figure 11 for Figure 4 The diagram shows the correlation between α / β and the energy efficiency improvement compared to a single-stage system in the pump assembly.

[0027] The reference numerals in the attached figures are as follows:

[0028] 11. First cylinder; 12. First vane; 13. First air inlet; 14. First roller; 21. Second cylinder; 22. Second vane; 23. Second air inlet; 24. Second roller; 3. Middle partition; 31. Main air inlet; 100. Compressor; 101. Exhaust port; 102. First intake port; 103. Second intake port; 201. Indoor windward side heat exchanger; 202. Indoor leeward side heat exchanger; 203. Outdoor heat exchanger; 301. First four-way reversing valve; 302. Second four-way reversing valve; 3021. Check valve; 400. First throttling element; 401. Second throttling element; 402. Third throttling element; 500. Flash evaporator. Detailed Implementation

[0029] See also Figures 1 to 11 As shown, according to an embodiment of the present invention, a pump assembly is provided for use in a dual-temperature air conditioning system, including a high-pressure compression section and a low-pressure compression section. The high-pressure compression section includes a first cylinder 11 and correspondingly disposed first vane 12 and first roller 14. The low-pressure compression section includes a second cylinder 21 and correspondingly disposed second vane 22 and second roller 24. The high-pressure compression section has a first air inlet 13, and the low-pressure compression section has a second air inlet 23. The projection onto a radial plane of the pump assembly (see details...) Figure 1As shown), the first sliding vane 12 and the second sliding vane 22 coincide, and the center line of the first air inlet 13 and the center line of the first sliding vane 12 have a first center angle β based on the center of the first cylinder 11, and the center line of the second air inlet 23 and the center line of the second sliding vane 22 have a second center angle α based on the center of the second cylinder 21, where α > β. In this technical solution, on the one hand, by misaligning the first air inlet 13 and the second air inlet 23 of the high-pressure compression section and the low-pressure compression section respectively on the axial projection of the pump body assembly, the different requirements of the high-pressure compression section and the low-pressure compression section in terms of cylinder air supply are adapted, thereby effectively improving the system energy efficiency (SEER). On the other hand, by setting corresponding air inlets for the high-pressure compression section and the low-pressure compression section respectively, without setting a separate air supply cylinder (i.e., the smallest diameter cylinder in the three-cylinder compressor), the manufacturing cost of the compressor is reduced. At the same time, when the compressor displacement is small, there is no need to consider the relationship between the air supply cylinder and the crankshaft diameter, resulting in a more compact structure that is conducive to the miniaturization design of the compressor and can improve the volumetric efficiency of the compressor. It is understood that the compressor corresponding to this embodiment is a quasi-two-stage compressor with dual intake and dual air supply. In addition, the included angle of α and β mentioned above in this invention covers the corresponding intake port.

[0030] The aforementioned air replenishment center line is specifically, for example, when the first air replenishment port 13 is a circular hole, it is the center of the circle, or when the first air replenishment port 13 is any other regular shape, such as a triangle or quadrilateral, it is the geometric center of the corresponding shape. The aforementioned symmetry center line refers to the symmetry center line of the slider in its sliding direction.

[0031] It is understandable that the specific locations of the first air inlet 13 and the second air inlet 23 should be after the corresponding compression section compresses the refrigerant to the corresponding intermediate pressure, and of course, they should also be located in the compression chamber before the exhaust pressure. The aforementioned intermediate pressure can be given according to the actual system requirements.

[0032] In a specific embodiment, such as Figure 9 As shown, 56°≤β≤238°; 63°≤α≤273°, and the specific design values ​​are obtained through comprehensive calculation based on parameters such as suction pressure, make-up pressure, discharge pressure, and compressor size. The aforementioned value range enables the corresponding compressor volumetric efficiency and system energy efficiency to be at a high level.

[0033] In some embodiments, when the pump assembly is applied to a dual-temperature air conditioning system and the dual-temperature air conditioning system is operating in cooling mode, the first cylinder 11 is connected in series with the indoor windward heat exchanger 201, and the second cylinder 21 is connected in series with the indoor leeward heat exchanger 202. The volume ratio of the first cylinder 11 to the second cylinder 21 is a, and the load ratio of the indoor windward heat exchanger 201 to the indoor leeward heat exchanger 202 is b, where 0.7 ≤ a / b ≤ 1.1. Preferably, a / b = 0.8. In a preferred embodiment, 0.9 ≤ a ≤ 1.3 (e.g., ...). Figure 10 (as shown); and / or, 0.72≤b≤1.04, the specific values ​​of the relevant parameters need to be reasonably selected based on the configuration of the selected heat exchanger. In this technical solution, the volume ratio of the two cylinders, the load ratio of the heat exchanger, and the ratio of the two mentioned above are limited, which can further improve the energy efficiency of the corresponding air conditioning system.

[0034] See Figure 3 As shown, a partition plate 3 is sandwiched between the first cylinder 11 and the second cylinder 21. The first air supply port 13 and the second air supply port 23 are respectively disposed on two opposite end faces of the partition plate 3. The partition plate 3 has an air supply channel communicating with the first air supply port 13 and the second air supply port 23. The air supply channel has a main air supply port 31 connected to an external air supply pipeline. By setting the air supply channel and the first air supply port 13 and the second air supply port 23 on the partition plate 3, air supply to the two cylinders can be achieved, which can further optimize the structure of the compressor.

[0035] See details Figure 4 As shown, the present invention also provides a pump body assembly, including a high-pressure compression section and a low-pressure compression section. The high-pressure compression section includes a first cylinder 11 and a corresponding first vane 12. The low-pressure compression section includes a second cylinder 21 and a corresponding second vane 22. One of the high-pressure and low-pressure compression sections has an air inlet. Projected onto a radial plane of the pump body assembly, the first vane 12 and the second vane 22 coincide. When the high-pressure compression section has an air inlet, the air inlet centerline and the symmetrical centerline of the first vane 12 form a first center angle β based on the center of the first cylinder 11, where 56° ≤ β ≤ 144° (see details). Figure 11 (as shown); or, when the low-pressure compression section has an air inlet, the air inlet's center line and the symmetrical center line of the second sliding vane 22 have a second center angle α based on the center of the second cylinder 21, 63°≤α≤166° (see details). Figure 11 (As shown). The specific design values ​​of α and β mentioned above are obtained through comprehensive calculation based on parameters such as suction pressure, make-up pressure, discharge pressure, and compressor size. The aforementioned value range enables the corresponding compressor volumetric efficiency and system energy efficiency to be at a high level. It is understood that the compressor corresponding to this embodiment is a quasi-two-stage compressor with dual suction and single make-up.

[0036] See Figure 5 As shown, a partition plate 3 is sandwiched between the first cylinder 11 and the second cylinder 21. An air supply port is located on one end face of the partition plate 3. The partition plate 3 contains an air supply channel communicating with the air supply port, and this channel has a main air supply port 31 connected to an external air supply pipeline. By placing the air supply channel and corresponding air supply ports (e.g., the first air supply port 13 or the second air supply port 23) on the partition plate 3, air supply to the low-pressure compression section or the high-pressure compression section can be achieved, further optimizing the compressor's structure.

[0037] According to an embodiment of the present invention, a compressor is also provided, including the pump body assembly described above.

[0038] According to an embodiment of the present invention, a dual-temperature air conditioning system is also provided, including a compressor 100, wherein the compressor 100 is the compressor described above. Specifically, the dual-temperature air conditioning system further includes a first four-way reversing valve 301, a second four-way reversing valve 302, an indoor airflow-facing heat exchanger 201, an indoor leeward heat exchanger 202, an outdoor heat exchanger 203, a first throttling element 400, and a flash evaporator 500. The D ports of the first four-way reversing valve 301 and the second four-way reversing valve 302 are connected to the exhaust port 101 of the compressor 100. The C port of the first four-way reversing valve 301 is connected to the end of the outdoor heat exchanger 203 away from the first throttling element 400. The E and S ports of the first four-way reversing valve 301 and the C port of the second four-way reversing valve 302 are connected to the end of the indoor airflow-facing heat exchanger 201 away from the first throttling element 400 and to the first intake port 102 of the high-pressure compressor section. The second four-way reversing valve 301... A one-way valve 3021 is provided on the C port connection branch of the directional valve 302. The one-way valve 3021 allows refrigerant to flow into the C port and cuts off in the reverse direction. The S port of the second four-way reversing valve 302 is connected to the second suction port 103 of the low-pressure compression section. The E port of the second four-way reversing valve 302 is connected to the end of the indoor leeward side heat exchanger 202 away from the first throttling element 400. The inlet of the flash evaporator 500 is connected to the end of the first throttling element 400 away from the outdoor heat exchanger 203. The make-up air outlet of the flash evaporator 500 is connected to the main make-up air port 31 of the pump body assembly. One outlet of the flash evaporator 500 is connected to the end of the indoor windward side heat exchanger 201 near the first throttling element 400. The other outlet of the flash evaporator 500 is connected to the end of the indoor leeward side heat exchanger 202 near the first throttling element 400. In this technical solution, by optimizing the design of each port of the two four-way valves and the one-way valve 3021, the system can meet the switching requirements of heating mode, cooling mode and reheat dehumidification mode of the dual-temperature air conditioning system, while simplifying the pipeline design and reducing the system construction cost (using only one one-way valve).

[0039] Regarding the operation of a dual-temperature air conditioning system, the following description uses a quasi-two-stage compressor with dual intake, dual replenishment, and single exhaust as an example. The operation of a dual-temperature air conditioning system using a quasi-two-stage compressor with dual intake, single replenishment, and single exhaust is basically the same, and will not be elaborated upon here.

[0040] When running in cooling mode, such as Figure 6 As shown, the first four-way reversing valve 301 and the second four-way reversing valve 302 are de-energized and in the first conducting state, with pipe E connected to pipe S and pipe C connected to pipe D. After the high-temperature and high-pressure exhaust gas from the compressor 100 is discharged, it flows through pipes D and C of the second four-way reversing valve 302 into the outdoor heat exchanger 203, where it condenses and releases heat. Then, after being throttled and depressurized by the first throttling element 400 (electronic expansion valve), it enters the flash evaporator 500. The throttled medium-pressure refrigerant flashes in the flash evaporator 500, with the gaseous refrigerant entering the first cylinder 11 and the second cylinder 21 through the main air supply port 31; the liquid refrigerant is divided into two paths: one path is throttled and depressurized by the third throttling element 402 and enters the indoor leeward side heat exchanger 202 for evaporation and heat absorption, and the gaseous refrigerant after evaporation and heat absorption... The refrigerant enters the second cylinder 21 through the E and S pipes of the second four-way reversing valve 302. After being compressed to an intermediate pressure within the second cylinder 21, it mixes with the medium-pressure refrigerant entering through the second air inlet 23 and continues to be compressed to a high-temperature, high-pressure refrigerant within the second cylinder 21. Another path leads to the refrigerant entering the indoor windward side heat exchanger 201 after being throttled and depressurized by the second throttling element 401. This gaseous refrigerant then evaporates and absorbs heat through the E and S pipes of the first four-way reversing valve 301. After being compressed to an intermediate pressure within the first cylinder 11, it mixes with the medium-pressure refrigerant entering through the first air inlet 13 and continues to be compressed to a high-temperature, high-pressure refrigerant. The high-temperature, high-pressure refrigerant from both the second cylinder 21 and the first cylinder 11 is then discharged together, completing the cycle.

[0041] When running in heating mode, such as Figure 7As shown, the first four-way reversing valve 301 and the second four-way reversing valve 302 are energized and are both in the second conducting state, with pipes D and E connected and pipes S and C connected. After the high-temperature and high-pressure exhaust gas from the compressor 100 is discharged, it splits into two paths. One path flows through pipes D and E of the second four-way reversing valve 302 and enters the indoor leeward side heat exchanger 202 for condensation and heat release. The condensed high-pressure liquid refrigerant is throttled and depressurized by the third throttling element 402. The other path flows through pipes D and E of the first four-way reversing valve 301 and enters the indoor windward side heat exchanger 201 for condensation and heat release. The condensed high-pressure liquid refrigerant is throttled and depressurized by the second throttling element 401. After throttling and depressurization, the two refrigerant streams merge and enter the flash evaporator 500 for flashing. The medium-pressure gaseous refrigerant in the flash evaporator 500 enters the first cylinder 11 and the second cylinder 21 via the main gas supply port 31. The liquid refrigerant, after being throttled and depressurized by the first throttling element 400, enters the outdoor heat exchanger 203 for evaporation and heat absorption. The gaseous refrigerant after evaporation and heat absorption splits into two streams: one stream enters the first cylinder 11 via the C and S pipes of the first four-way reversing valve 301 and is compressed to medium pressure, then mixes with the medium-pressure refrigerant entering via the first gas supply port 13 and continues to be compressed to high temperature and high pressure within the first cylinder 11; the other stream enters the second cylinder 21 via the C and S pipes of the one-way valve 3021 and the second four-way reversing valve 302 and is compressed to medium pressure, then mixes with the medium-pressure refrigerant entering via the second gas supply port 23 and continues to be compressed to high temperature and high pressure within the second cylinder 21. The high-temperature, high-pressure refrigerant compressed by the second cylinder 21 and the first cylinder 11 is discharged together, completing the cycle.

[0042] When running in reheat dehumidification mode, such as Figure 8As shown, the second four-way reversing valve 302 is energized, connecting pipes D and E, and pipes C and S; the first four-way reversing valve 301 is de-energized, connecting pipes D and C, and pipes E and S. After the high-temperature and high-pressure exhaust from the compressor 100 is discharged, it splits into two paths. One path flows through pipes D and E of the second four-way reversing valve 302 and enters the indoor leeward side heat exchanger 202 for condensation and heat release. The condensed high-pressure liquid refrigerant is throttled and depressurized by the third throttling element 402. The other path flows through pipes D and C of the first four-way reversing valve 301 and enters the outdoor heat exchanger 203 for condensation and heat release. The condensed high-pressure liquid refrigerant is throttled and depressurized by the first throttling element 400 and then enters the flash evaporator 500 for flash evaporation. The gaseous refrigerant in the flash evaporator 500 enters the first cylinder 11 and the second cylinder 21 through the main air inlet 31. The liquid refrigerant, after being throttled and depressurized by the third throttling element 402, merges with the liquid refrigerant and then, after being throttled and depressurized by the second throttling element 401, enters the indoor windward heat exchanger 201 for evaporation and heat absorption. The gaseous refrigerant after evaporation and heat absorption flows in two paths: one path enters the first cylinder 11 through the E and S pipes of the first four-way reversing valve 301 for compression. After being compressed to medium pressure, it mixes with the medium-pressure refrigerant entering through the first air inlet 13 and is further compressed to high temperature and high pressure within the first cylinder 11; the other path enters the second cylinder 21 through the one-way valve 3021 for compression. After being compressed to medium pressure, it mixes with the medium-pressure refrigerant entering through the second air inlet 23 and is further compressed to high temperature and high pressure within the second cylinder 21. The high-temperature and high-pressure gaseous refrigerant compressed by the second cylinder 21 and the first cylinder 11 is discharged together, completing the cycle.

[0043] It will be readily understood by those skilled in the art that the aforementioned advantageous methods can be freely combined and superimposed without conflict.

[0044] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present invention should be included within the protection scope of the present invention. The above are merely preferred embodiments of the present invention. It should be noted that for those skilled in the art, several improvements and modifications can be made without departing from the technical principles of the present invention, and these improvements and modifications should also be considered within the protection scope of the present invention.

Claims

1. A pump body assembly, comprising a high-pressure compression section and a low-pressure compression section, wherein, The high-pressure compression section includes a first cylinder (11) and a first sliding vane (12) corresponding to it, and the low-pressure compression section includes a second cylinder (21) and a second sliding vane (22) corresponding to it. The high-pressure compression section has a first air inlet (13), and the low-pressure compression section has a second air inlet (23). Projected on a radial plane of the pump body assembly, the first sliding vane (12) and the second sliding vane (22) coincide. The air inlet center line of the first air inlet (13) and the center line of symmetry of the first sliding vane (12) have a first center angle β based on the center of the first cylinder (11). The air inlet center line of the second air inlet (23) and the center line of symmetry of the second sliding vane (22) have a second center angle α based on the center of the second cylinder (21). α > β, 56° ≤ β ≤ 238°. 63°≤α≤273°; When the pump assembly is applied to a dual-temperature air conditioning system and the dual-temperature air conditioning system is in cooling mode, the first cylinder (11) is connected in series with the indoor windward heat exchanger (201), the second cylinder (21) is connected in series with the indoor leeward heat exchanger (202), the volume ratio of the first cylinder (11) to the second cylinder (21) is a, the load ratio of the indoor windward heat exchanger (201) to the indoor leeward heat exchanger (202) is b, 0.7≤a / b≤1.

1.

2. The pump body assembly according to claim 1, characterized in that, 0.9≤a≤1.3; and / or, 0.72≤b≤1.04; and / or, a / b=0.

8.

3. The pump body assembly according to claim 1, characterized in that, A partition plate (3) is sandwiched between the first cylinder (11) and the second cylinder (21). The first air inlet (13) and the second air inlet (23) are respectively disposed on the two opposite end faces of the partition plate (3). The partition plate (3) has an air supply channel that communicates with the first air inlet (13) and the second air inlet (23). The air supply channel has a main air supply port (31) that is connected to an external air supply pipeline.

4. A compressor, characterized in that, The pump body assembly includes any one of claims 1 to 3.

5. A dual-temperature air conditioning system, characterized in that, Includes a compressor (100), wherein the compressor (100) is the compressor of claim 4.

6. The dual-temperature air conditioning system according to claim 5, characterized in that, It also includes a first four-way reversing valve (301), a second four-way reversing valve (302), an indoor windward heat exchanger (201), an indoor leeward heat exchanger (202), an outdoor heat exchanger (203), and a first throttling element (400). The first four-way reversing valve (301) and the second four-way reversing valve (302) each have a D port that is connected to the exhaust port (101) of the compressor (100). The C port of the first four-way reversing valve (301) is connected to the end of the outdoor heat exchanger (203) away from the first throttling element (400). The E port and S port of the first four-way reversing valve (301) and the second four-way reversing valve (302) are also connected. The C port of the second four-way reversing valve (302) is connected to the end of the indoor windward heat exchanger (201) away from the first throttling element (400) and to the first suction port (102) of the high-pressure compression section. A one-way valve (3021) is provided on the C port connection branch of the second four-way reversing valve (302). The one-way valve (3021) allows refrigerant to flow into the C port and cuts off in the reverse direction. The S port of the second four-way reversing valve (302) is connected to the second suction port (103) of the low-pressure compression section. The E port of the second four-way reversing valve (302) is connected to the end of the indoor leeward heat exchanger (202) away from the first throttling element (400).

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