WO2024016748A1 - 泵体组件、压缩机、双温空调系统 - Google Patents

泵体组件、压缩机、双温空调系统 Download PDF

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Publication number
WO2024016748A1
WO2024016748A1 PCT/CN2023/087846 CN2023087846W WO2024016748A1 WO 2024016748 A1 WO2024016748 A1 WO 2024016748A1 CN 2023087846 W CN2023087846 W CN 2023087846W WO 2024016748 A1 WO2024016748 A1 WO 2024016748A1
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WIPO (PCT)
Prior art keywords
air supply
cylinder
supply port
port
compression part
Prior art date
Application number
PCT/CN2023/087846
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English (en)
French (fr)
Inventor
梁祥飞
吕如兵
张健伟
霍喜军
秦静
Original Assignee
珠海格力电器股份有限公司
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Publication of WO2024016748A1 publication Critical patent/WO2024016748A1/zh

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member

Definitions

  • the present disclosure belongs to the technical field of air conditioning, and specifically relates to a pump body assembly, a compressor, and a dual-temperature air conditioning system.
  • the functions of the air conditioning system have evolved from a single temperature adjustment to become more diversified to meet people's ever-increasing needs for comfort in the living environment.
  • the main dehumidification method of the air conditioning system is refrigeration dehumidification, which means that the surface temperature of the indoor heat exchanger is reduced to below the air dew point temperature.
  • This method is suitable for high-temperature environments. It can complete indoor cooling while dehumidifying.
  • a three-cylinder dual-temperature parallel air-conditioning system is proposed.
  • This air-conditioning system can realize indoor dual-temperature cascade heat exchange in cooling mode.
  • the parallel cylinders can effectively reduce the dryness of the evaporator inlet and increase the cooling capacity of the indoor evaporator.
  • the system also has a reheat dehumidification function to achieve dehumidification without cooling during transition seasons.
  • this solution uses a three-cylinder compressor and has a separate air supply cylinder for air supply, the cost is high.
  • the small cylinder air supply cylinder
  • the small cylinder is limited by the diameter of the crankshaft, and the cylinder diameter of the small cylinder cannot be miniaturized.
  • the cylinder parameters cannot achieve optimal design, resulting in low volumetric efficiency, large mechanical damage, and poor system performance.
  • a dual evaporation temperature that is, dual temperature
  • the suction air of the two cylinders The pressures are not the same.
  • the angles between the air supply ports of the two cylinders and the corresponding slide vanes are obviously not suitable for the needs of the dual-temperature air conditioning system. It is necessary to adjust the two cylinders.
  • the aforementioned angles of respective cylinders are optimized, and the present disclosure is proposed to solve the aforementioned problems.
  • the present disclosure provides a pump body assembly, a compressor, and a dual-temperature air conditioning system, which can overcome the high manufacturing cost of the compressor caused by the separate installation of a supplementary cylinder in the related art, and the limitation of the compressor's small size design due to the limitation of the crankshaft diameter of the supplementary cylinder. shortcomings.
  • the present disclosure provides a pump body assembly, including a high-pressure compression part and a low-pressure compression part, wherein the high-pressure compression part includes a first cylinder and a first sliding vane provided corresponding thereto, and the low-pressure compression part includes The second cylinder and its corresponding second sliding vane, the high compression part has a first air supply port, the low pressure compression part has a second air supply port, projected on a radial surface of the pump body assembly, the third A sliding piece coincides with the second sliding piece, and there is a first center clamp based on the center of the first cylinder between the air supply center line of the first air supply port and the symmetrical center line of the first sliding piece.
  • Angle ⁇ , the air supply center line of the second air supply port and the symmetrical center line of the second slide plate have a second center angle ⁇ based on the center of the second cylinder, ⁇ > ⁇ .
  • the first cylinder is connected in series with the indoor windward side heat exchanger
  • the second cylinder is connected with the indoor windward side heat exchanger.
  • the leeward side heat exchangers are connected in series
  • the volume ratio of the first cylinder to the second cylinder is a
  • the load ratio of the indoor windward side heat exchanger to the indoor leeward side heat exchanger is b, 0.7 ⁇ a /b ⁇ 1.1.
  • 0.9 ⁇ a ⁇ 1.3; and/or, 0.72 ⁇ b ⁇ 1.04; and/or, a/b 0.8.
  • a middle partition is sandwiched between the first cylinder and the second cylinder, and the first air supply port and the second air supply port are respectively provided on opposite sides of the middle partition.
  • an air supply channel is constructed in the middle partition plate and is connected to the first air supply port and the second air supply port.
  • the air supply channel has a main air supply port connected to an external air supply pipeline.
  • the present disclosure also provides a pump body assembly, including a high-pressure compression part and a low-pressure compression part, wherein the high-pressure compression part includes a first cylinder and a first sliding vane provided corresponding thereto, and the low-pressure compression part includes a second cylinder and a There is a corresponding second sliding plate, one of the high compression part and the low pressure compression part has an air supply port, projected on a radial surface of the pump body assembly, the first sliding plate and the second sliding plate When the high-pressure compression part has the air supply port, there is a first air supply center line based on the center of the first cylinder between the air supply center line of the air supply port and the symmetrical center line of the first sliding vane.
  • the second center angle ⁇ between the centers of the two cylinders is 63° ⁇ 166°.
  • a middle partition is sandwiched between the first cylinder and the second cylinder, the air supply port is provided on one end surface of the middle partition, and a middle partition is constructed inside the middle partition.
  • An air supply channel is connected with the air supply port, and the air supply channel has a main air supply port connected with an external air supply pipeline.
  • the present disclosure also provides a compressor, including the above-mentioned pump body assembly.
  • the present disclosure also provides a dual-temperature air conditioning system, including a compressor, and the compressor is the above-mentioned compressor.
  • the dual-temperature air conditioning system further includes a first four-way reversing valve, a second four-way reversing valve, an indoor windward side heat exchanger, an indoor leeward side heat exchanger, an outdoor heat exchanger, and a third Throttle element, wherein the D ports of the first four-way reversing valve and the second four-way reversing valve are collectively connected to the exhaust port of the compressor, and the first four-way reversing valve Port C of the valve is connected to an end of the outdoor heat exchanger away from the first throttling element, and ports E and S of the first four-way reversing valve and port C of the second four-way reversing valve are combined.
  • Port C of the second four-way reversing valve is connected to the A one-way valve is provided on the road.
  • the one-way valve allows the refrigerant to flow into the C port and blocks it in the reverse direction.
  • the S port of the second four-way reversing valve is connected to the second suction port of the low-pressure compression part.
  • the E port of the second four-way reversing valve is connected to an end of the indoor leeward side heat exchanger away from the first throttling element.
  • the present disclosure provides a pump body assembly, a compressor, and a dual-temperature air conditioning system.
  • the first air supply port and the second air supply port respectively provided by the high-pressure compression part and the low-pressure compression part are projected in the axial direction of the pump body assembly.
  • the misalignment is formed on the high-pressure compression section and the low-pressure compression section to adapt to the different suction pressure requirements of the high-pressure compression section and the low-pressure compression section, thereby effectively improving the system energy efficiency (SEER); on the other hand, corresponding corresponding pressures are set for both the high-pressure compression section and the low-pressure compression section.
  • SEER system energy efficiency
  • the air supply port does not require a separate air supply cylinder (that is, the smallest diameter cylinder in the three-cylinder compressor), which reduces the manufacturing cost of the compressor.
  • a separate air supply cylinder that is, the smallest diameter cylinder in the three-cylinder compressor
  • the parameters of the first cylinder and the second cylinder are optimized and the structure is more compact, which is beneficial to the miniaturization design of the compressor and can improve the volumetric efficiency of the compressor.
  • Figure 1 is a schematic structural diagram (schematic diagram) of the pump body assembly along its axial projection according to an embodiment of the present disclosure
  • Figure 2 is a schematic diagram (schematic diagram) of the internal structure of a compressor according to another embodiment of the present disclosure
  • Figure 3 is a schematic structural diagram of the middle partition in Figure 2;
  • Figure 4 is a schematic diagram (schematic diagram) of the internal structure of a compressor according to yet another embodiment of the present disclosure
  • Figure 5 is a schematic structural diagram of the middle partition in Figure 4.
  • Figure 6 is a schematic diagram of the dual-temperature air conditioning system in the cooling mode according to the embodiment of the present disclosure (including a schematic diagram of the refrigerant flow direction);
  • Figure 7 is a schematic diagram of the dual-temperature air conditioning system in the heating mode according to the embodiment of the present disclosure (including a schematic diagram of the refrigerant flow direction);
  • Figure 8 is a schematic diagram of the dual-temperature air conditioning system in the dehumidification and reheat mode according to the embodiment of the present disclosure (including a schematic diagram of the refrigerant flow direction);
  • Figure 9 is a schematic diagram showing the correlation between ⁇ / ⁇ in the pump assembly shown in Figure 1 and the energy efficiency improvement compared to the single-stage system;
  • Figure 10 is a schematic diagram of the correlation curve between the volume ratio a and the relative optimal value ratio
  • Figure 11 is a schematic diagram showing the correlation between ⁇ / ⁇ in the pump assembly shown in Figure 4 and the energy efficiency improvement compared with the single-stage system.
  • the reference symbols are expressed as: 11. The first cylinder; 12. The first sliding vane; 13. The first air supply port; 14. The first roller; 21. The second cylinder; 22. The second sliding vane; 23. The second air supply port; 24. The second Two rollers; 3. Middle partition; 31. Main air supply port; 100. Compressor; 101. Exhaust port; 102. First air suction port; 103. Second air suction port; 201. Indoor windward side heat exchange 202. Indoor leeward side heat exchanger; 203. Outdoor heat exchanger; 301. First four-way reversing valve; 302. Second four-way reversing valve; 3021. One-way valve; 400. First throttling Component; 401, second throttling component; 402, third throttling component; 500, flasher.
  • a pump assembly which is used in a dual-temperature air conditioning system and includes a high-pressure compression part and a low-pressure compression part, where the high-pressure compression part includes a first cylinder. 11 and the first sliding plate 12 and the first roller 14 arranged correspondingly.
  • the low-pressure compression part includes the second cylinder 21 and the second sliding plate 22 and the second roller 24 arranged correspondingly.
  • the high-pressure part has a first compensation
  • the air port 13 the low-pressure compression part has a second air supply port 23, which is projected on a radial surface of the pump body assembly (see Figure 1 for details).
  • the first sliding plate 12 and the second sliding plate 22 overlap, and the first air supply port Between the air supply centerline of 13 and the symmetrical centerline of the first slide 12 there is a gap based on the center of the first cylinder 11 There is a first central included angle ⁇ , and a second central included angle ⁇ based on the center of the second cylinder 21, ⁇ > ⁇ , between the air supply center line of the second air supply port 23 and the symmetrical center line of the second sliding plate 22.
  • the compression section has different needs in terms of cylinder air supply volume, which can effectively improve the system energy efficiency (SEER); on the other hand, corresponding air supply ports are set up for both the high-pressure compression section and the low-pressure compression section, without separate air supply cylinders (i.e. (the smallest diameter cylinder among three-cylinder compressors), which reduces the manufacturing cost of the compressor.
  • SEER system energy efficiency
  • corresponding air supply ports are set up for both the high-pressure compression section and the low-pressure compression section, without separate air supply cylinders (i.e. (the smallest diameter cylinder among three-cylinder compressors), which reduces the manufacturing cost of the compressor.
  • SEER system energy efficiency
  • the aforementioned air supply center line is specifically, for example, when the first air supply port 13 is a circular hole, it is the center of the circle, or when the first air supply port 13 is any other regular shape, such as a triangle, a quadrilateral, etc., It is the geometric center of the corresponding shape, and the aforementioned center line of symmetry refers to the center line of symmetry of the slide in its sliding direction.
  • first air supply port 13 and the second air supply port 23 should be after the corresponding compression section compresses the refrigerant to the corresponding intermediate pressure, and of course should also be at a position covered by the compression chamber before the exhaust pressure. , the aforementioned intermediate pressure can be given according to the actual system requirements.
  • the first cylinder 11 is connected in series with the indoor windward side heat exchanger 201
  • the second cylinder 21 is connected with the indoor leeward side heat exchanger.
  • Heaters 202 are connected in series
  • the volume ratio of the first cylinder 11 and the second cylinder 21 is a
  • 0.9 ⁇ a ⁇ 1.3 (as shown in Figure 10); and/or, 0.72 ⁇ b ⁇ 1.04.
  • a middle partition 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 provided on two opposite end surfaces of the middle partition 3.
  • middle partition 3 An air supply channel is constructed inside that communicates 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.
  • the present disclosure also provides a pump body assembly, which includes a high-pressure compression part and a low-pressure compression part.
  • the high-pressure compression part includes a first cylinder 11 and a first sliding vane 12 provided corresponding thereto.
  • the low-pressure compression part The part includes a second cylinder 21 and a second sliding vane 22 arranged corresponding thereto.
  • One of the high compression part and the low pressure compression part has an air supply port, which is projected on a radial surface of the pump body assembly.
  • the first sliding vane 12 and The second sliding vane 22 overlaps.
  • the air supply center line of the air supply port and the symmetrical center line of the first sliding vane 12 have a first center angle ⁇ based on the center of the first cylinder 11 , 56° ⁇ 144° (see Figure 11 for details); or, when the low-pressure compression part has an air supply port, the air supply center line of the air supply port and the symmetrical center line of the second sliding vane 22 have a relationship based on the third
  • the second center angle ⁇ between the centers of the two cylinders 21 is 63° ⁇ 166° (see Figure 11 for details).
  • the specific design values of the aforementioned ⁇ and ⁇ are comprehensively calculated based on parameters such as suction pressure, air supply pressure, exhaust pressure, and compressor size.
  • the aforementioned value range can keep the corresponding compressor volumetric efficiency and system energy efficiency at a high level. It can be understood that the corresponding compressor in this embodiment is a quasi-two-stage compressor with dual suction and single supplementary air.
  • a middle partition plate 3 is sandwiched between the first cylinder 11 and the second cylinder 21.
  • the air supply port is provided on one end surface of the middle partition plate 3.
  • the middle partition plate 3 is configured with a gas supply port connected to the air supply port.
  • the air supply channel has a main air supply port 31 connected with an external air supply pipeline.
  • a compressor is also provided, including the above-mentioned pump body assembly.
  • a dual-temperature air conditioning system including a compressor 100, and the compressor 100 is the above-mentioned compressor.
  • the dual-temperature air conditioning system also includes a first four-way reversing valve 301, a second four-way reversing valve 302, an indoor windward side heat exchanger 201, an indoor leeward side heat exchanger 202, an outdoor heat exchanger 203, and Throttle element 400 and flasher 500, wherein the D ports of the first four-way reversing valve 301 and the second four-way reversing valve 302 are collectively connected to the exhaust port 101 of the compressor 100, and the first four-way reversing valve 302 Port C of the reversing valve 301 is connected to the end of the outdoor heat exchanger 203 away from the first throttling element 400 , port E and port S of the first four-way reversing valve 301 and port C of the second four-way reversing valve 302 It is connected
  • the C-port connection branch of the second four-way reversing valve 302 is provided with One-way valve 3021, one-way The valve 3021 allows the refrigerant to flow into the C port and blocks it 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 part.
  • the E port of the second four-way reversing valve 302 is connected to the indoor space.
  • the leeward side heat exchanger 202 is connected at one end away from the first throttling element 400.
  • the inlet of the flasher 500 is connected to the end of the first throttling element 400 away from the outdoor heat exchanger 203.
  • the air supply outlet of the flasher 500 is connected to the pump.
  • the main air supply port 31 of the body assembly is connected, one outlet of the flasher 500 is connected with one end of the indoor windward side heat exchanger 201 close to the first throttling element 400, and the other outlet of the flasher 500 exchanges heat with the indoor leeward side.
  • the end of the device 202 close to the first throttling element 400 is connected.
  • the operation process of the dual-temperature air conditioning system the following is a detailed description of the quasi-two-stage compressor with dual suction, dual supplementary air, and single exhaust.
  • the dual-temperature quasi-two-stage compressor with dual suction, single supplementary air, and single exhaust is applied.
  • the operation process of the air conditioning system is basically the same as this, and will not be described in detail in this disclosure:
  • the first four-way reversing valve 301 and the second four-way reversing valve 302 are powered off and in the first conduction state.
  • the E pipe is connected to the S pipe, and the C pipe is connected to the S pipe.
  • D tube is conductive.
  • the high-temperature and high-pressure exhaust gas from the compressor 100 is discharged, it flows through the D and C pipes of the second four-way reversing valve 302 and enters the outdoor heat exchanger 203. It is condensed and released in the outdoor heat exchanger 203, and then passes through the first
  • the throttling element 400 electronic expansion valve
  • the throttled medium-pressure refrigerant flashes in the flasher 500, and the gaseous refrigerant enters the first cylinder through the main air supply port 31. 11 and the second cylinder 21; the liquid refrigerant is divided into two paths: one path passes through the throttling and decompression of the third throttling element 402 and then enters the indoor leeward side heat exchanger 202 for evaporation and heat absorption. After evaporation and heat absorption, the gaseous refrigerant is refrigerated. The refrigerant enters the second cylinder 21 through the E pipe and S pipe of the second four-way reversing valve 302.
  • the medium-pressure refrigerant entering through the second air supply port 23 is mixed and then flows through the second cylinder 21.
  • the cylinder 21 continues to be compressed to high temperature and high pressure refrigerant; the other path is throttled and decompressed by the second throttling element 401 and then enters the indoor windward side heat exchanger 201 to evaporate and absorb heat.
  • the gaseous refrigerant after evaporating and absorbing heat passes through the first
  • the E-pipe and S-pipe of the four-way reversing valve 301 enter the first cylinder 11 of the compressor.
  • the medium-pressure refrigerant entering through the first air supply port 13 is mixed and continues to be compressed to high temperature and high pressure. refrigerant.
  • the high-temperature and high-pressure refrigerant passing through the second cylinder 21 and the first cylinder 11 are discharged together to complete the cycle.
  • the first four-way reversing valve 301 and the second four-way reversing valve 302 are energized and both are in the second conduction state.
  • the D pipe is connected to the E pipe, and the S pipe is connected. It is connected to the C pipe; after the high-temperature and high-pressure exhaust gas from the compressor 100 is discharged, it is divided into two paths, flowing through the D and E pipes of the second four-way reversing valve 302, and then enters the indoor leeward side heat exchanger 202 for condensation and discharge.
  • the hot, condensed high-pressure liquid refrigerant is The three throttling elements 402 perform throttling and pressure reduction; the other path passes through the D pipe and E pipe 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 passes through the third The two throttling elements 401 perform throttling and pressure reduction. After throttling and decompressing, the two-channel refrigerant merges and enters the generator 500 for flashing.
  • the medium-pressure gas refrigerant main air supply port 31 in the flasher 500 enters the first cylinder 11 and the second cylinder 21; the liquid refrigerant passes through The first throttling element 400 throttles and reduces the pressure and then enters the outdoor heat exchanger 203 to evaporate and absorb heat.
  • the gaseous refrigerant after evaporation and heat absorption is divided into two paths: one passes through the C pipe and S pipe of the first four-way reversing valve 301 and enters the first cylinder 11 and is compressed to medium-pressure refrigerant; and the other passes through the first air supply port 13.
  • the medium-pressure refrigerant After the medium-pressure refrigerant is mixed, it continues to be compressed into high-temperature and high-pressure refrigerant in the first cylinder 11; the other path passes through the one-way valve 3021 and the C pipe and S pipe of the second four-way reversing valve 302 and enters the second cylinder 21 to be compressed into the middle pressure refrigerant.
  • the compressed refrigerant is mixed with the intermediate-pressure refrigerant entering through the second air supply port 23 and then continues to be compressed into high-temperature and high-pressure refrigerant in the second cylinder 21 .
  • the high-temperature and high-pressure refrigerant compressed by the second cylinder 21 and the first cylinder 11 are discharged together to complete the cycle.
  • the second four-way reversing valve 302 When running in the reheat dehumidification mode, as shown in Figure 8, the second four-way reversing valve 302 is powered on, the D pipe and E pipe are connected, and the C pipe and S pipe are connected; the first four-way reversing valve 301 is powered off. , the D pipe is connected to the C pipe, and the E pipe is connected to the S pipe; after the high-temperature and high-pressure exhaust gas from the compressor 100 is discharged, it is divided into two paths and flows through the D and E pipes of the second four-way reversing valve 302. It enters the indoor leeward side heat exchanger 202 for condensation and heat release.
  • the condensed high-pressure liquid refrigerant passes through the third throttling element 402 for throttling and pressure reduction; the other path passes through the D and C tubes of the first four-way reversing valve 301 , enters the outdoor heat exchanger 203 for condensation and heat release.
  • the condensed high-pressure liquid refrigerant is throttled and decompressed by the first throttling element 400 and then enters the flash device 500 for flashing.
  • the gaseous refrigerant in the flash generator 500 enters the first cylinder 11 and the second cylinder 21 through the main air supply port 31; after the liquid refrigerant merges with the refrigerant that has been throttled and depressurized by the third throttling element 402, it passes through the second cylinder.
  • the throttling element 401 throttles and reduces the pressure and then enters the indoor windward side heat exchanger 201 for evaporation and heat absorption.
  • the gaseous refrigerant flow after evaporation and heat absorption is divided into two paths: one path passes through the E pipe and S pipe of the first four-way reversing valve 301 and enters the first cylinder 11 for compression. After being compressed to medium pressure, it enters the first air supply port 13. After the medium-pressure refrigerant is mixed, it is further compressed into a high-temperature and high-pressure refrigerant in the first cylinder 11; the other path enters the second cylinder 21 through the one-way valve 3021 for compression.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Compression-Type Refrigeration Machines With Reversible Cycles (AREA)

Abstract

泵体组件、压缩机以及双温空调系统。泵体组件包括高压压缩部与低压压缩部，高压压缩部包括第一气缸（11）以及与其对应设置的第一滑片（12），低压压缩部包括第二气缸（21）以及与其对应设置的第二滑片（22），高压压缩部具有第一补气口（13），低压压缩部具有第二补气口（23），第一补气口（13）的补气中心线与第一滑片（12）的对称中心线之间具有基于第一气缸（11）的中心的第一中心夹角β，第二补气口（23）的补气中心线与第二滑片（22）的对称中心线之间具有基于第二气缸（21）的中心的第二中心夹角α，α＞β。该泵体组件通过第一补气口和第二补气口在泵体组件的轴向投影上形成错位提高系统效能。

Description

泵体组件、压缩机、双温空调系统
本公开要求于2022年07月18日提交中国专利局、申请号为202210842633.1、发明名称为“泵体组件、压缩机、双温空调系统”的中国专利申请的优先权，其全部内容通过引用结合在本公开中。
技术领域
本公开属于空气调节技术领域，具体涉及一种泵体组件、压缩机、双温空调系统。
背景技术
空调系统作为调节环境舒适性的装置，其功能已从单一的温度调节发展的更加多样化，用以满足人们不断提高的生活环境舒适性的需求。目前空调系统的主要除湿方式为制冷除湿，即将室内换热器表面温度降至空气露点温度以下，当室内空气流过换热器表面时，空气中的水蒸气将发生冷凝，将空气水分去除。该方式适用于高温环境，除湿的同时完成室内降温，但在长江流域的“梅雨季节”或华南地区的“回南天”时期，温度不高但相对湿度较高的情况，常规家用变频空调在过渡季制冷除湿时，室内回风温度和回风露点逐渐降低，室内相对湿度降至一定程度后不再降低甚至反而升高，导致室内冷而不干；另一方面，蒸发温度和回风露点降低导致空调的单位能耗除湿量显著降低。因此，在过渡季潮湿天气时，常规家用变频空调制冷除湿无法满足除湿的舒适性需求，通常处于闲置状态。
相关技术中提出一种三缸双温并行的空调系统，该空调系统在制冷模式下能实现室内双温梯级换热，并行缸能有效降低蒸发器入口干度，提高室内蒸发器的制冷量，提升制冷能效比，该系统还具备再热除湿功能，实现过渡季节除湿不降温的功能。但该方案由于采用三缸压缩机，单独设置了补气缸进行补气，其成本较高，在总排量较低时小缸(补气缸)受曲轴直径限制，小缸气缸直径无法小型化、气缸参数无法达到最优设计，导致其容积效率低、机械损伤大，系统性能较差；同时，在双蒸发温度(也即双温)空调系统中，两气缸的吸气 压力并不相同，相关技术中的常规双缸准二级压缩机，两气缸的补气口与相对应的滑片之间的角度相同显然与双温空调系统的需求不相适应，有必要对两缸分别的前述角度进行优化，针对前述问题，提出本公开。
发明内容
因此，本公开提供一种泵体组件、压缩机、双温空调系统，能够克服相关技术中单独设置补气缸导致压缩机制造成本偏高、补气缸受限于曲轴直径大小压缩机无法小型化设计的不足。
为了解决上述问题，本公开提供一种泵体组件，包括高压压缩部与低压压缩部，其中，所述高压压缩部包括第一气缸以及与其对应设置的第一滑片，所述低压压缩部包括第二气缸以及与其对应设置的第二滑片，所述高压缩部具有第一补气口，所述低压压缩部具有第二补气口，在泵体组件的一径向面上投影，所述第一滑片与所述第二滑片重合，所述第一补气口的补气中心线与所述第一滑片的对称中心线之间具有基于所述第一气缸的中心的第一中心夹角β，所述第二补气口的补气中心线与所述第二滑片的对称中心线之间具有基于所述第二气缸的中心的第二中心夹角α，α＞β。
在一些实施方式中，56°≤β≤238°；和/或，63°≤α≤273°。
在一些实施方式中，当所述泵体组件应用于双温空调系统中且双温空调系统运行制冷模式时，所述第一气缸与室内迎风侧换热器串联，所述第二气缸与室内背风侧换热器串联，所述第一气缸与所述第二气缸的容积比为a，所述室内迎风侧换热器与所述室内背风侧换热器的负荷比为b，0.7≤a/b≤1.1。
在一些实施方式中，0.9≤a≤1.3；和/或，0.72≤b≤1.04；和/或，a/b＝0.8。
在一些实施方式中，所述第一气缸与所述第二气缸之间夹设有中隔板，所述第一补气口与所述第二补气口分别设置于所述中隔板的相对两个端面上，所述中隔板内构造有与所述第一补气口及第二补气口连通的补气通道，所述补气通道具有与外部补气管路连接的总补气口。
本公开还提供一种泵体组件，包括高压压缩部与低压压缩部，其中，所述高压压缩部包括第一气缸以及与其对应设置的第一滑片，所述低压压缩部包括第二气缸以及与其对应设置的第二滑片，所述高压缩部及低压压缩部中的一个上具有补气口，在泵体组件的一径向面上投影，所述第一滑片与所述第二滑片重合，当所述高压压缩部具有所述补气口时，所述补气口的补气中心线与所述第一滑片的对称中心线之间具有基于所述第一气缸的中心的第一中心夹角β， 56°≤β≤144°；或者，当所述低压压缩部具有所述补气口时，所述补气口的补气中心线与所述第二滑片的对称中心线之间具有基于所述第二气缸的中心的第二中心夹角α，63°≤α≤166°。
在一些实施方式中，所述第一气缸与所述第二气缸之间夹设有中隔板，所述补气口设置于所述中隔板的一个端面上，所述中隔板内构造有与所述补气口连通的补气通道，所述补气通道具有与外部补气管路连接的总补气口。
本公开还提供一种压缩机，包括上述的泵体组件。
本公开还提供一种双温空调系统，包括压缩机，所述压缩机为上述的压缩机。
在一些实施方式中，所述双温空调系统还包括第一四通换向阀、第二四通换向阀、室内迎风侧换热器、室内背风侧换热器、室外换热器、第一节流元件，其中所述第一四通换向阀与所述第二四通换向阀分别具有的D口汇总连通于所述压缩机的排气口，所述第一四通换向阀的C口与所述室外换热器远离所述第一节流元件的一端连通，所述第一四通换向阀的E口、S口以及第二四通换向阀的C口汇总与所述室内迎风侧换热器远离所述第一节流元件的一端连通且与所述高压压缩部具有的第一吸气口连通，所述第二四通换向阀的C口连接支路上设有单向阀，所述单向阀允许冷媒流入所述C口而反向截止，所述第二四通换向阀的S口与所述低压压缩部具有的第二吸气口连通，所述第二四通换向阀的E口与所述室内背风侧换热器远离所述第一节流元件的一端连通。
本公开提供的一种泵体组件、压缩机、双温空调系统，一方面，通过将高压压缩部与低压压缩部分别具有的第一补气口及第二补气口在泵体组件的轴向投影上形成错位，适应了高压压缩部以及低压压缩部在吸气压力方面的不同需求，从而能够有效提高系统能效(SEER)；另一方面，针对高压压缩部与低压压缩部两者分别设置相应的补气口，不单独设置补气缸(也即三缸压缩机中的直径最小缸)，降低了压缩机的制造成本，同时在压缩机排量较小时，无需顾及补气缸与曲轴直径的关系，可以对第一气缸及第二气缸的参数进行优化设计，结构更加紧凑有利于压缩机的小型化设计，且能够提高压缩机容积效率。
附图说明
图1为本公开实施例的泵体组件沿其轴向投影的结构示意图(简略示意图)；
图2为本公开另一实施例的压缩机的内部结构示意图(简略示意图)；
图3为图2中的中隔板的结构示意图；
图4为本公开又一实施例的压缩机的内部结构示意图(简略示意图)；
图5为图4中的中隔板的结构示意图；
图6为本公开实施例的双温空调系统处于制冷模式下的状态示意图(含冷媒流向示意)；
图7为本公开实施例的双温空调系统处于制热模式下的状态示意图(含冷媒流向示意)；
图8为本公开实施例的双温空调系统处于除湿再热模式下的状态示意图(含冷媒流向示意)；
图9为图1所示的泵体组件中α/β与相较于单级系统能效提升幅度的相关性示意图；
图10为容积比a与相对最优值占比的相关性曲线示意图；
图11为图4所示的泵体组件中α/β与相较于单级系统能效提升幅度的相关性示意图。
附图标记表示为：
11、第一气缸；12、第一滑片；13、第一补气口；14、第一滚子；21、第
二气缸；22、第二滑片；23、第二补气口；24、第二滚子；3、中隔板；31、总补气口；100、压缩机；101、排气口；102、第一吸气口；103、第二吸气口；201、室内迎风侧换热器；202、室内背风侧换热器；203、室外换热器；301、第一四通换向阀；302、第二四通换向阀；3021、单向阀；400、第一节流元件；401、第二节流元件；402、第三节流元件；500、闪发器。
具体实施方式
结合参见图1至图11所示，根据本公开的实施例，提供一种泵体组件，应用于双温空调系统中，包括高压压缩部与低压压缩部，其中，高压压缩部包括第一气缸11以及与其对应设置的第一滑片12、第一滚子14，低压压缩部包括第二气缸21以及与其对应设置的第二滑片22、第二滚子24，高压缩部具有第一补气口13，低压压缩部具有第二补气口23，在泵体组件的一径向面上投影(具体参见图1所示)，第一滑片12与第二滑片22重合，第一补气口13的补气中心线与第一滑片12的对称中心线之间具有基于第一气缸11的中心的 第一中心夹角β，第二补气口23的补气中心线与第二滑片22的对称中心线之间具有基于第二气缸21的中心的第二中心夹角α，α＞β。该技术方案中，一方面，通过将高压压缩部与低压压缩部分别具有的第一补气口13及第二补气口23在泵体组件的轴向投影上形成错位，适应了高压压缩部以及低压压缩部在气缸补气量方面的不同需求，从而能够有效提高系统能效(SEER)；另一方面，针对高压压缩部与低压压缩部两者分别设置相应的补气口，不单独设置补气缸(也即三缸压缩机中的直径最小缸)，降低了压缩机的制造成本，同时在压缩机排量较小时，无需顾及补气缸与曲轴直径的关系，结构更加紧凑有利于压缩机的小型化设计，且能够提高压缩机容积效率。能够理解的，该实施例下对应的压缩机为双吸气双补气的准二级压缩机。另外，本公开的前述α及β的夹角覆盖了相应的吸气口。
前述的补气中心线具体例如当第一补气口13为一圆形孔时，其为该圆形的圆心，或者当第一补气口13为任一其他的规则形状时例如三角形、四边形等，其为相应的形状的几何中心，前述的对称中心线则指滑片在其滑动方向上的对称中心线。
能够理解的是，第一补气口13以及第二补气口23的具体设置位置应该处于相应的压缩部对冷媒压缩至对应的中间压力之后，当然还应处于排气压力之前的压缩腔涵盖的位置处，前述的中间压力根据实际的系统需求给出即可。
在一个具体的实施例中，如图9所示，56°≤β≤238°；63°≤α≤273°，而具体的设计取值根据吸气压力、补气压力、排气压力、压缩机尺寸等参数综合计算获得。前述取值范围能够使相应的压缩机容积效率以及系统能效处于较高的水平。
在一些实施方式中，当泵体组件应用于双温空调系统中且双温空调系统运行制冷模式时，第一气缸11与室内迎风侧换热器201串联，第二气缸21与室内背风侧换热器202串联，第一气缸11与第二气缸21的容积比为a，室内迎风侧换热器201与室内背风侧换热器202的负荷比为b，0.7≤a/b≤1.1，在一些实施方式中，a/b＝0.8，在一些实施方式中，0.9≤a≤1.3(如图10所示)；和/或，0.72≤b≤1.04，具体的相关参数的取值需依据具体选用的换热器的配置合理选择。该技术方案中，对两个气缸的容积比、换热器的负荷比以及前述两者的比值进行了限定，能够进一步提高相应的空调系统的能效。
参见图3所示出，第一气缸11与第二气缸21之间夹设有中隔板3，第一补气口13与第二补气口23分别设置于中隔板3的相对两个端面上，中隔板3 内构造有与第一补气口13及第二补气口23连通的补气通道，补气通道具有与外部补气管路连接的总补气口31。通过将补气通道以及第一补气口13、第二补气口23设置于中隔板3上，实现对两个气缸的补气，能够进一步优化压缩机的结构。
具体参见图4所示出，本公开还提供一种泵体组件，包括高压压缩部与低压压缩部，其中，高压压缩部包括第一气缸11以及与其对应设置的第一滑片12，低压压缩部包括第二气缸21以及与其对应设置的第二滑片22，高压缩部及低压压缩部中的一个上具有补气口，在泵体组件的一径向面上投影，第一滑片12与第二滑片22重合，当高压压缩部具有补气口时，补气口的补气中心线与第一滑片12的对称中心线之间具有基于第一气缸11的中心的第一中心夹角β，56°≤β≤144°(具体参见图11所示)；或者，当低压压缩部具有补气口时，补气口的补气中心线与第二滑片22的对称中心线之间具有基于第二气缸21的中心的第二中心夹角α，63°≤α≤166°(具体参见图11所示)。前述的α、β的具体设计取值根据吸气压力、补气压力、排气压力、压缩机尺寸等参数综合计算获得。前述取值范围能够使相应的压缩机容积效率以及系统能效处于较高的水平。能够理解的，该实施例下对应的压缩机为双吸气单补气的准二级压缩机。
参见图5所示出，第一气缸11与第二气缸21之间夹设有中隔板3，补气口设置于中隔板3的一个端面上，中隔板3内构造有与补气口连通的补气通道，补气通道具有与外部补气管路连接的总补气口31。通过将补气通道以及相应的补气口(例如第一补气口13或者第二补气口23)设置于中隔板3上，实现对低压压缩部或者高压压缩部的补气，能够进一步优化压缩机的结构。
根据本公开的实施例，还提供一种压缩机，包括上述的泵体组件。
根据本公开的实施例，还提供一种双温空调系统，包括压缩机100，压缩机100为上述的压缩机。具体的，双温空调系统还包括第一四通换向阀301、第二四通换向阀302、室内迎风侧换热器201、室内背风侧换热器202、室外换热器203、第一节流元件400、闪发器500，其中第一四通换向阀301与第二四通换向阀302分别具有的D口汇总连通于压缩机100的排气口101，第一四通换向阀301的C口与室外换热器203远离第一节流元件400的一端连通，第一四通换向阀301的E口、S口以及第二四通换向阀302的C口汇总与室内迎风侧换热器201远离第一节流元件400的一端连通且与高压压缩部具有的第一吸气口102连通，第二四通换向阀302的C口连接支路上设有单向阀3021，单向 阀3021允许冷媒流入C口而反向截止，第二四通换向阀302的S口与低压压缩部具有的第二吸气口103连通，第二四通换向阀302的E口与室内背风侧换热器202远离第一节流元件400的一端连通，闪发器500的入口与第一节流元件400远离室外换热器203的一端连接，闪发器500的补气出口与泵体组件的总补气口31连通，闪发器500的一出口与室内迎风侧换热器201靠近第一节流元件400的一端连通，闪发器500的另一出口则与室内背风侧换热器202靠近第一节流元件400的一端连通。该技术方案中，通过对两个四通的各个管口以及单向阀3021的优化设计，在实现双温空调系统制热模式、制冷模式以及再热除湿模式切换需求的同时，简化了管路设计，降低了系统构建成本(仅用一个单向阀)。
关于双温空调系统的运行过程，以下结合双吸气双补气单排气的准二级压缩机进行具体阐述，而双吸气单补气单排气的准二级压缩机应用的双温空调系统的运行过程与此基本相同，本公开不做赘述：
在制冷模式运行时，如图6所示，第一四通换向阀301及第二四通换向阀302断电，处于第一导通状态，E管与S管导通，C管与D管导通。压缩机100的高温高压排气排出后，流经第二四通换向阀302的D管、C管进入室外换热器203，在室外换热器203内进行冷凝放热，接着经第一节流元件400(电子膨胀阀)节流降压后进入闪发器500，节流后的中压制冷剂在闪发器500内闪发，其中气态制冷剂通过总补气口31进入第一气缸11及第二气缸21内；液态制冷剂分两路：一路通过第三节流元件402的节流降压后进入室内背风侧换热器202进行蒸发吸热，经蒸发吸热后的气态制冷剂经第二四通换向阀302的E管、S管进入第二气缸21，在第二气缸21内压缩至中间压力后由第二补气口23进入的中压制冷剂混合后在第二气缸21内继续压缩至高温高压制冷剂；另一路经第二节流元件401节流降压后进入室内迎风侧换热器201进行蒸发吸热，经蒸发吸热后的气态制冷剂经第一四通换向阀301的E管、S管进入压缩机第一气缸11，在第一气缸11内压缩至中间压力后由第一补气口13进入的中压制冷剂混合后继续压缩至高温高压制冷剂。经第二气缸21及第一气缸11的高温高压制冷剂一起排出，完成循环。
在制热模式运行时，如图7所示，第一四通换向阀301及第二四通换向阀302通电，均处于第二导通状态，D管与E管导通，S管与C管导通；压缩机100的高温高压排气排出后，分两路，一路流经第二四通换向阀302的D管、E管，进入室内背风侧换热器202进行冷凝放热，冷凝后的高压液态制冷剂经第 三节流元件402进行节流降压；另一路经第一四通换向阀301的D管、E管，进入室内迎风侧换热器201进行冷凝放热，冷凝后的高压液态制冷剂经第二节流元件401进行节流降压。节流降压后的两路制冷剂汇合进入闪发器500闪发，在闪发器500内的中压气态制冷剂总补气口31进入第一气缸11、第二气缸21；液态制冷剂经第一节流元件400节流降压后进入室外换热器203进行蒸发吸热。经蒸发吸热后的气态制冷剂分两路：一路经第一四通换向阀301的C管、S管进入第一气缸11压缩至中压制冷剂后与经第一补气口13进入的中压制冷剂混合后在第一气缸11内继续压缩至高温高压制冷剂；另一路经单向阀3021、第二四通换向阀302的C管、S管进入第二气缸21压缩至中压制冷剂后与经第二补气口23进入的中压制冷剂混合后在第二气缸21内继续压缩至高温高压制冷剂。经第二气缸21及第一气缸11压缩的高温高压制冷剂一起排出，完成循环。
在再热除湿模式运行时，如图8所示，第二四通换向阀302通电，D管和E管导通，C管和S管导通；第一四通换向阀301断电，D管与C管导通，E管与S管导通；压缩机100的高温高压排气排出后，分两路，一路流经第二四通换向阀302的D管、E管，进入室内背风侧换热器202进行冷凝放热，冷凝后的高压液态制冷剂经第三节流元件402进行节流降压；另一路经第一四通换向阀301的D管、C管，进入室外换热器203进行冷凝放热，冷凝后的高压液态制冷剂经第一节流元件400进行节流降压后进入闪发器500进行闪发。闪发器500内的气态制冷剂经总补气口31进入第一气缸11、第二气缸21；液态制冷剂与经第三节流元件402节流降压后的制冷剂汇合后，通过第二节流元件401节流降压后进入室内迎风侧换热器201进行蒸发吸热。蒸发吸热后的气态制冷剂流分两路：一路经第一四通换向阀301的E管及S管进入第一气缸11进行压缩，压缩至中压后与第一补气口13进入的中压制冷剂混合后在第一气缸11内进一步压缩至高温高压制冷剂；另一路经单向阀3021进入第二气缸21进行压缩，压缩至中压后与通过第二补气口23进入的中压制冷剂混合后在第二气缸21内进一步压缩至高温高压制冷剂。经第二气缸21及第一气缸11压缩后的高温高压气态制冷剂一起排出，完成循环。
本领域的技术人员容易理解的是，在不冲突的前提下，上述各有利方式可以自由地组合、叠加。
以上仅为本公开的较佳实施例而已，并不用以限制本公开，凡在本公开的精神和原则之内所作的任何修改、等同替换和改进等，均应包含在本公开的保 护范围之内。以上仅是本公开的优选实施方式，应当指出，对于本技术领域的普通技术人员来说，在不脱离本公开技术原理的前提下，还可以做出若干改进和变型，这些改进和变型也应视为本公开的保护范围。

Claims (13)

  1. 一种泵体组件，包括高压压缩部与低压压缩部，其中，所述高压压缩部包括第一气缸(11)以及与其对应设置的第一滑片(12)，所述低压压缩部包括第二气缸(21)以及与其对应设置的第二滑片(22)，所述高压缩部具有第一补气口(13)，所述低压压缩部具有第二补气口(23)，在泵体组件的一径向面上投影，所述第一滑片(12)与所述第二滑片(22)重合，所述第一补气口(13)的补气中心线与所述第一滑片(12)的对称中心线之间具有基于所述第一气缸(11)的中心的第一中心夹角β，所述第二补气口(23)的补气中心线与所述第二滑片(22)的对称中心线之间具有基于所述第二气缸(21)的中心的第二中心夹角α，α＞β。
  2. 根据权利要求1所述的泵体组件，其中，56°≤β≤238°。
  3. 根据权利要求1所述的泵体组件，其中，63°≤α≤273°。
  4. 根据权利要求1所述的泵体组件，其中，当所述泵体组件应用于双温空调系统中且双温空调系统运行制冷模式时，所述第一气缸(11)与室内迎风侧换热器(201)串联，所述第二气缸(21)与室内背风侧换热器(202)串联，所述第一气缸(11)与所述第二气缸(21)的容积比为a，所述室内迎风侧换热器(201)与所述室内背风侧换热器(202)的负荷比为b，0.7≤a/b≤1.1。
  5. 根据权利要求3所述的泵体组件，其中，0.9≤a≤1.3。
  6. 根据权利要求3所述的泵体组件，其中，0.72≤b≤1.04。
  7. 根据权利要求3所述的泵体组件，其中，a/b＝0.8。
  8. 根据权利要求1所述的泵体组件，其中，所述第一气缸(11)与所述第二气缸(21)之间夹设有中隔板(3)，所述第一补气口(13)与所述第二补气口(23)分别设置于所述中隔板(3)的相对两个端面上，所述中隔板(3)内构造有与所述第一补气口(13)及第二补气口(23)连通的补气通道，所述补气通道具有与外部补气管路连接的总补气口(31)。
  9. 一种泵体组件，包括高压压缩部与低压压缩部，其中，所述高压压缩部包括第一气缸(11)以及与其对应设置的第一滑片(12)，所述低压压缩部包括第二气缸(21)以及与其对应设置的第二滑片(22)，所述高压缩部及低压压缩部中的一个上具有补气口，在泵体组件的一径向面上投影，所述第一滑片(12)与所述第二滑片(22)重合，当所述高压压缩部具有所述补气口时，所述补气口的补气中心线与所述第一滑片(12)的对称中心线之间具有基于所述第一气缸(11)的中心的第一中心夹角β，56°≤β≤144°；或者，当所述 低压压缩部具有所述补气口时，所述补气口的补气中心线与所述第二滑片(22)的对称中心线之间具有基于所述第二气缸(21)的中心的第二中心夹角α，63°≤α≤166°。
  10. 根据权利要求9所述的泵体组件，其中，所述第一气缸(11)与所述第二气缸(21)之间夹设有中隔板(3)，所述补气口设置于所述中隔板(3)的一个端面上，所述中隔板(3)内构造有与所述补气口连通的补气通道，所述补气通道具有与外部补气管路连接的总补气口(31)。
  11. 一种压缩机，包括权利要求1至10中任一项所述的泵体组件。
  12. 一种双温空调系统，包括压缩机(100)，所述压缩机(100)为权利要求11所述的压缩机。
  13. 根据权利要求12所述的双温空调系统，其中，还包括第一四通换向阀(301)、第二四通换向阀(302)、室内迎风侧换热器(201)、室内背风侧换热器(202)、室外换热器(203)、第一节流元件(400)，其中所述第一四通换向阀(301)与所述第二四通换向阀(302)分别具有的D口汇总连通于所述压缩机(100)的排气口(101)，所述第一四通换向阀(301)的C口与所述室外换热器(203)远离所述第一节流元件(400)的一端连通，所述第一四通换向阀(301)的E口、S口以及第二四通换向阀(302)的C口汇总与所述室内迎风侧换热器(201)远离所述第一节流元件(400)的一端连通且与所述高压压缩部具有的第一吸气口(102)连通，所述第二四通换向阀(302)的C口连接支路上设有单向阀(3021)，所述单向阀(3021)允许冷媒流入所述C口而反向截止，所述第二四通换向阀(302)的S口与所述低压压缩部具有的第二吸气口(103)连通，所述第二四通换向阀(302)的E口与所述室内背风侧换热器(202)远离所述第一节流元件(400)的一端连通。
PCT/CN2023/087846 2022-07-18 2023-04-12 泵体组件、压缩机、双温空调系统 WO2024016748A1 (zh)

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