WO2020181764A1 - 气液分离器、压缩机组件及空调器 - Google Patents

气液分离器、压缩机组件及空调器 Download PDF

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Publication number
WO2020181764A1
WO2020181764A1 PCT/CN2019/110745 CN2019110745W WO2020181764A1 WO 2020181764 A1 WO2020181764 A1 WO 2020181764A1 CN 2019110745 W CN2019110745 W CN 2019110745W WO 2020181764 A1 WO2020181764 A1 WO 2020181764A1
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WO
WIPO (PCT)
Prior art keywords
gas
liquid separator
outlet pipe
compressor
housing
Prior art date
Application number
PCT/CN2019/110745
Other languages
English (en)
French (fr)
Inventor
胡余生
魏会军
余冰
王珺
杨欧翔
张心爱
Original Assignee
珠海格力电器股份有限公司
珠海格力节能环保制冷技术研究中心有限公司
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Application filed by 珠海格力电器股份有限公司, 珠海格力节能环保制冷技术研究中心有限公司 filed Critical 珠海格力电器股份有限公司
Priority to EP19918921.8A priority Critical patent/EP3879208A4/en
Publication of WO2020181764A1 publication Critical patent/WO2020181764A1/zh

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    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/026—Lubricant separation
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/02—Compressor arrangements of motor-compressor units
    • F25B31/023—Compressor arrangements of motor-compressor units with compressor of reciprocating-piston type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
    • F25B43/006—Accumulators
    • 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
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • 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
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/12—Vibration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
    • F25B2400/07—Details of compressors or related parts
    • F25B2400/074—Details of compressors or related parts with multiple cylinders
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/13—Vibrations
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/16—Lubrication

Definitions

  • This application relates to the technical field of air conditioners, in particular to a gas-liquid separator, a compressor assembly and an air conditioner.
  • the suction frequency of this type of compressor is equivalent to the suction resonance frequency (the suction frequency of the compressor is generally not Greater than the suction resonance frequency), the pressure wave generated by the resonance of the refrigerant produces a suction boost effect on the suction of the compressor, which in turn increases the amount of refrigerant sucked into the compressor, and enhances the compression performance of the compressor.
  • C is the speed of sound propagation in the refrigerant (m/s)
  • L is the length of the outlet pipe where the refrigerant flows (m)
  • V is the compressor displacement (m 3 )
  • A is the outlet pipe’s Cross-sectional area (m 2 ).
  • the existing compressors are developing toward higher and higher compression frequencies, that is, the suction frequency of the compressor is getting higher and higher, which causes the suction frequency of the compressor to exceed the suction resonance frequency, resulting in the compressor
  • the resonance pulsation of the refrigerant cannot be used to achieve the effect of suction and boost, and the suction volume of the compressor is reduced, resulting in deterioration of the performance of the compressor.
  • the first-order refrigerant can be increased by reducing the length L of the outlet pipe, reducing the compressor displacement V or increasing the cross-sectional area A of the outlet pipe Resonance frequency f, where the compressor displacement V and the outlet pipe cross-sectional area A have a small influence on the first-order resonance frequency f of the refrigerant, and the outlet pipe length L has a greater influence on the first-order resonance frequency f of the refrigerant.
  • the patent with publication number CN205349734U describes a technical solution in which the outlet pipe penetrates from the side wall of the gas-liquid separator housing to the outside of the housing, so that only the length of the outlet pipe can be reduced without Shortening the length of the outlet pipe L of the gas-liquid separator does not affect the capacity of the gas-liquid separator.
  • this is likely to cause oil accumulation in the area below the outlet pipe of the gas-liquid separator and reduce the lubricating oil in the compressor.
  • This affects the reliability of the compressor's long-term operation; in addition, since the outlet pipe penetrates from the side wall of the gas-liquid separator to the outside of the casing, most of the outlet pipe hangs and extends into the inner cavity of the gas-liquid separator. This makes the outlet pipe prone to greater vibration when the compressor is running, which can easily lead to increased noise, and may even cause damage and fracture of the outlet pipe.
  • the main purpose of this application is to provide a gas-liquid separator that facilitates the improvement of high-frequency compression performance and facilitates the return of lubricating oil.
  • the gas-liquid separator provided by the present application includes a casing, an outlet pipe and a suction pipe.
  • the outlet pipe extends into the inner cavity of the gas-liquid separator and penetrates from the side wall of the casing to the outside of the casing.
  • One end of the suction pipe extends to the bottom of the inner cavity of the gas-liquid separator, and the other end of the suction pipe is connected with the outlet pipe.
  • the suction frequency of the high-frequency compressor is equivalent, which is convenient for the compressor to produce a suction and boost effect during high-frequency operation, so as to enhance the intake efficiency of the compressor and enhance the performance of the compressor; in addition, the setting of the suction pipe facilitates the The lubricating oil at the bottom of the separator is sucked into the compressor to prevent a large amount of lubricating oil from accumulating at the bottom of the inner cavity of the gas-liquid separator, so that the compressor is continuously lubricated, and the compressor is guaranteed to operate reliably for a long time.
  • the outlet pipe has an inner extension section and an outer section, the inner extension section is located in the inner cavity of the gas-liquid separator, the outer section penetrates from the side wall of the housing to the outside of the housing, and the suction tube is connected to the outer section .
  • a further solution is that the inner extension section extends in a vertical direction.
  • a further solution is that the circumscribed section extends in a horizontal direction.
  • Another preferred solution is that there are two outlet pipes, and at least one outlet pipe penetrates from the side wall of the housing to the outside of the housing.
  • outlet pipe penetrates from the first position of the side wall of the housing to the outside of the housing, and the distance between the first position and the bottom end of the housing is not greater than the distance between the first position and the top end of the housing.
  • the gas-liquid separator further includes a fixing member located in the inner cavity of the gas-liquid separator, and the fixing member is fixedly connected to the casing and the outlet pipe.
  • outlet pipe penetrates from the first position of the side wall of the housing to the outside of the housing, and the outlet pipe and the fixing member are connected to the second position, along the vertical direction, the first position is separated from the second position by a first distance , The end of the outlet pipe extending to the top of the inner cavity of the gas-liquid separator is separated from the first position by a second distance, and the ratio of the first distance to the second distance is 0.3 to 0.7.
  • cross-sectional area of the suction pipe is significantly smaller than the cross-sectional area of the outlet pipe.
  • this can prevent a large amount of liquid from flowing into the compressor and avoid liquid shock to the compressor.
  • it also enables the compressor to suck in lubricating oil through the suction pipe for a long time, which helps to ensure the long-term reliable operation of the compressor.
  • Another object of the present application is to provide a gas-liquid separator that facilitates the improvement of high-frequency compression performance and facilitates the return of lubricating oil.
  • the compressor assembly includes a compressor and a gas-liquid separator.
  • the gas-liquid separator includes a casing, an outlet pipe and a suction pipe, and the outlet pipe extends into the inner cavity of the gas-liquid separator.
  • the outlet pipe penetrates from the side wall of the housing to the outside of the housing, one end of the suction pipe extends to the bottom of the inner cavity of the gas-liquid separator, and the other end of the suction pipe is communicated with the fluid inlet of the compressor.
  • the first-order resonance frequency prevents the suction frequency of the compressor from significantly exceeding the first-order resonance frequency of the refrigerant during high-frequency operation, so that the compressor can effectively utilize the suction and boost effect during high-frequency operation to enhance the compressor intake Efficiency, enhance the performance of the compressor; in addition, the setting of the suction pipe facilitates sucking the lubricating oil at the bottom of the gas-liquid separator into the compressor, avoiding a large amount of lubricating oil from accumulating at the bottom of the inner cavity of the gas-liquid separator, so that the compressor can be continuously lubricated , To ensure the long-term reliable operation of the compressor.
  • Another object of the present application is to provide a compressor assembly with good compressor high-frequency compression performance and convenient lubricating oil return.
  • the compressor assembly provided by the present application includes a compressor and the aforementioned gas-liquid separator, and an end of the outlet pipe that passes through the shell is connected to the compressor.
  • the compressor assembly of the present application adopts the aforementioned gas-liquid separator, so that the suction efficiency of the compressor during high-frequency operation is improved, which is conducive to improving the high-frequency operation performance of the compressor. In addition, it is also conducive to Ensure long-term reliable operation of the compressor.
  • Another object of the present application is to provide a compressor assembly with good compressor high-frequency compression performance and convenient lubricating oil return.
  • the compressor assembly provided by the present application includes a compressor, a connector, and the aforementioned gas-liquid separator.
  • the outlet pipe is fixedly connected to the housing at a position where the outlet pipe passes through.
  • the end outside the casing is fixedly connected to the compressor, and the connecting piece is fixedly connected between the compressor casing and the casing; along the vertical direction, the outlet pipe is fixedly connected to the first height position of the casing, and the fixing piece is fixedly connected At the second height position of the casing, the connecting member is fixedly connected to the third height position of the casing, and the second height position is located between the first height position and the third height position.
  • the compressor assembly of the present application adopts the aforementioned gas-liquid separator, so that the suction efficiency of the compressor during high-frequency operation is improved, which is beneficial to improve the high-frequency operation performance of the compressor, and also helps to ensure compression
  • the second height position is set between the first height position and the third height position, so that the vibration of the extension section is transmitted to the cylinder between the first height position and the third height position through the fixing member. It is beneficial to enhance the connection rigidity of the inner extension section, reduce the vibration intensity of the inner extension section, and reduce the vibration intensity of the gas-liquid separator.
  • Another object of the present application is to provide an air conditioner with good compressor high frequency compression performance and convenient lubricating oil return.
  • the air conditioner provided in the present application includes the aforementioned compressor assembly.
  • the compressor assembly of the present application adopts the aforementioned compressor, so that the suction efficiency of the compressor during high-frequency operation is improved, which is conducive to improving the high-frequency operation performance of the compressor, and is conducive to improving the high-frequency operation of the air conditioner.
  • Frequency performance in addition, is also conducive to ensuring the long-term reliable operation of the compressor and the long-term reliable operation of the air conditioner.
  • Figure 1 is a cross-sectional view of a gas-liquid separator in a prior art case
  • Figure 2 is a sectional view of a compressor assembly of a prior art case
  • FIG. 3 is a cross-sectional view of the first embodiment of the gas-liquid separator of the present application.
  • Embodiment 4 is a cross-sectional view of Embodiment 1 of the compressor assembly of the present application.
  • FIG. 5 is a cross-sectional view of the second embodiment of the gas-liquid separator of the present application.
  • FIG. 6 is a cross-sectional view of the third embodiment of the gas-liquid separator of the present application.
  • Fig. 7 is a graph showing the vibration of the bottom shell of the gas-liquid separator of the present application as a function of the ratio of H1/H0;
  • Fig. 8 is a graph showing the vibration of the first outlet pipe of the gas-liquid separator of the present application as a function of the ratio of H3/H2.
  • Example one of gas-liquid separator, compressor assembly and air conditioner is shown.
  • the air conditioner of this embodiment is equipped with the compressor assembly of this embodiment.
  • the compressor assembly of this embodiment includes a compressor 200 and a gas-liquid separator 100 of this embodiment.
  • the gas-liquid separator 100 includes a housing, a first outlet pipe 103 and a suction pipe 104.
  • the housing includes a cylinder 101 and a bottom housing 105.
  • the bottom housing 105 is fixed to the bottom of the cylinder 101.
  • the first outlet pipe 103 has a vertical
  • the inner extension section 131 extending in the straight direction and the outer section 133 extending in the horizontal direction are connected by a curved section 132 between the inner extension section 131 and the outer section 133.
  • the inner extension section 131 and the curved section 132 are both located in the gas-liquid separator 100 In the inner cavity, the inner extending section 131 extends to the top of the inner cavity of the gas-liquid separator 100, the outer section 133 penetrates from the side wall of the cylinder 101 to the outside of the casing, and the outer section 133 is fixed to the casing of the compressor 200 by welding.
  • the outer section 133 and the cylinder 101 are fixed by welding, one end of the liquid suction tube 104 extends to the bottom of the inner cavity of the gas-liquid separator 100, and the other end of the liquid suction tube 104 is connected to the outer section 133.
  • the fixing member 102 is fixedly connected to the cylinder 101.
  • the fixing member 102 is located in the inner cavity of the gas-liquid separator 100.
  • the fixing member 102 and The inner extension of the first outlet pipe 103 is fixedly connected.
  • the setting of the suction pipe 104 facilitates sucking the lubricating oil at the bottom of the inner cavity of the gas-liquid separator 100 into the compressor, avoiding a large amount of lubricating oil accumulating at the bottom of the inner cavity of the gas-liquid separator 100, so that the compressor can continue to get Lubrication ensures long-term reliable operation of the compressor.
  • the cylinder 101 and the casing of the compressor 200 are also fixed by a connecting piece 500.
  • the cylinder 101 and the casing of the compressor 200 are both welded to the connecting piece 500 in the vertical direction,
  • the connecting piece 500 is located above the outer section 133, so that there are two fixed connections between the cylinder 101 and the casing of the compressor 200, which is beneficial to make the fixed connection between the gas-liquid separator 100 and the compressor 100 more stable and reliable.
  • the outer section 133 is fixedly connected to the first height position of the cylinder body 101
  • the fixing member 102 is fixedly connected to the second height position of the cylinder body 101
  • the connecting member 500 is fixedly connected to the third height position of the cylinder body 101. Since the first height position and the third height position of the cylinder body 101 are fixedly connected to the casing of the compressor 200, the area between the first height position and the third height position of the cylinder body 101 has better resistance.
  • the second height position is set between the first height position and the third height position, so that the vibration of the extension section 131 is transmitted to the first height position and the third height position of the cylinder 101 through the fixing member 102 In between, it is beneficial to enhance the connection rigidity of the inner extension 131, reduce the vibration intensity of the inner extension 131, and reduce the vibration intensity of the gas-liquid separator 100.
  • the connecting piece 500 and the cylinder 101 can also be fixedly connected by one or more methods such as clamps and screws.
  • the connecting piece 500 and the casing of the compressor 200 can also be fixedly connected.
  • the fixed connection can be made by one or more methods such as clamps and screws.
  • the suction pipe 104 may also be directly connected to the fluid inlet of the compressor, and the suction pipe 104 and the first outlet pipe 103 operate separately.
  • the inwardly extending section 131 and the externally extending section 133 are connected by a bending section 132, which is beneficial to avoid stress concentration at the connection between the inwardly extending section 131 and the externally extending section 133, and improve the anti-vibration performance of the first outlet pipe 103.
  • the compressor 200 is a two-cylinder compressor, and the gas-liquid separator 100 also has a second outlet pipe.
  • the first outlet pipe 103 and the second outlet pipe 106 each have an inward section 131 extending in the vertical direction and The circumscribed section 133 extending in the direction.
  • the first outlet pipe 103 and the second outlet pipe 106 are both round pipes.
  • the top end of the second outlet pipe 106 is flush with the top end of the first outlet pipe 103, the outer section 133 of the second outlet pipe 106 is located below the outer pipe of the first outlet pipe 103, and the pipe axis of the outer section 133 of the second outlet pipe 106 The distance from the pipe axis of the circumscribed section 133 of the first outlet pipe 103 is H4.
  • the outer section 133 penetrates from the side wall of the cylinder 101 to the outside of the casing, the outer section 133 is fixed to the cylinder 101 at the passing position, and the outer section 133 is no longer fixed with the bottom shell 105 of the gas-liquid separator 100, and the gas-liquid separation
  • the bottom shell 105 of the gas-liquid separator 100 is prone to large vibrations.
  • this embodiment is simulated on the Ansys simulation software under different conditions where H1/H0 is between 0.2 and 0.7.
  • the relative value of the maximum vibration value b of the bottom shell 105 is 1.
  • the maximum vibration value b of the bottom shell 105 is a/b, and the value of a/b is the relative vibration value of the bottom shell 105 of the gas-liquid separator 100 when the corresponding value is H1/H0), and H1/H0 is between 0.2 and Curves of relative vibration values of the bottom shell 105 of the gas-liquid separator 100 under different conditions within the range of 0.7 are shown in FIG. 7.
  • H1/H0 it is more preferable to limit H1/H0 to be between 0.4 and 0.5 In this way, the relationship between the length L1 of the first outlet pipe 103 and the vibration intensity of the bottom shell 105 of the gas-liquid separator 100 can be balanced as much as possible, which is conducive to the use of suction and boosting of the compressor, and improves the performance of the compressor. It is possible to reduce the vibration of the gas-liquid separator 100 and reduce the operating noise of the compressor.
  • this embodiment simulates the top end of the extension section 131 and the bending section 132 on the Ansys simulation software at H3/H2 between 0.1
  • the relative value is 1, when H3/H2 is other value, the maximum vibration value of the top end of the extension section 131 or the bending section 132 is c, then c/d is the top end of the extension section 131 or the bending section 132 under the condition of H3/H2
  • the relative vibration value of H3/H2 is in the range of 0.1 to 0.9.
  • the relative vibration value curve of the top end of the extension section 131 and the bending section 132 under different conditions is shown in Fig
  • the gas-liquid separator 300 in the prior art two-cylinder compressor, includes a third outlet pipe 303 and a fourth outlet pipe 306, the third outlet pipe 303 and the fourth outlet pipe 306
  • the bottom shell of the liquid separator 300 penetrates out of the shell, and is then fixedly connected to the casing of the compressor 400.
  • the total height of the shell of the gas-liquid separator 300 is set to H5, and the pipe axis of the outer section 333 of the third outlet pipe 303 The distance from the bottom of the bottom shell is H6, the distance between the pipe axis of the outer section 333 of the third outlet pipe 303 and the top end of the inward section 331 is H7, the pipe axis of the outer section 333 of the third outlet pipe 303 and the fixing member 102 The distance is H8.
  • the top end of the fourth outlet pipe 306 is flush with the top end of the third outlet pipe 303, the outer section of the fourth outlet pipe 306 is located below the outer section 333 of the third outlet pipe 303, and the pipe axis of the outer section of the fourth outlet pipe 306 is aligned with The pipe axis of the circumscribed section 333 of the third outlet pipe 303 is H9 apart.
  • the effective volume of the gas-liquid separator 100 of this technical solution embodiment is significantly larger than that of the gas-liquid separator 300 of the prior art case Effective volume, the volumetric efficiency of the compressor is significantly improved, and the vibration and noise of the gas-liquid separator 100 of the technical solution of this embodiment are significantly weaker than those of the gas-liquid separator 300 in the prior art.
  • the first outlet pipe 103 penetrates from the side wall of the cylinder 101 to the outside of the shell, and the second outlet pipe 106 penetrates from the bottom shell 105 to the outside of the shell, which can shorten the first outlet pipe to a certain extent.
  • the lengths of 103 and the second outlet pipe 103 increase the suction resonance frequency in the inner cavity of the gas-liquid separator 100.
  • the rest of the second embodiment of the gas-liquid separator, compressor assembly and air conditioner is the same as the first embodiment of the gas-liquid separator, compressor assembly and air conditioner.
  • Embodiment three of gas-liquid separator, compressor assembly and air conditioner is the same.
  • the gas-liquid separator 100 has only the first outlet pipe 103, and the gas-liquid separator 100 of this embodiment is used for a single-cylinder compressor.
  • the rest of the third embodiment of the gas-liquid separator, compressor assembly and air conditioner is the same as the first embodiment of the gas-liquid separator, compressor assembly and air conditioner.

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  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
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  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

一种气液分离器（100），包括壳体、出口管（103）和吸液管（104），出口管（103）从壳体的侧壁穿出至壳体外，吸液管（104）的一端伸至气液分离器（100）的内腔底部，吸液管（104）的另一端与出口管（103）连接。还公开了一种压缩机组件和空调器。通过减短出口管（103）的长度，可以提升制冷剂的一阶共振频率，避免压缩机高频运行时的吸气频率明显超出制冷剂的一阶共振频率，便于压缩机在高频运行时产生抽吸增压效果，增强压缩机的进气效率，提高压缩机的性能。

Description

气液分离器、压缩机组件及空调器
相关申请的交叉引用
本申请要求于2019年3月13日提交中国专利局，申请号为201910188182.2，申请名称为“气液分离器、压缩机组件及空调器”的中国专利申请的优先权,在此将其全文引入作为参考。
技术领域
本申请涉及空调技术领域，具体是涉及一种气液分离器、压缩机组件及空调器。
背景技术
现有技术中已知有利用抽吸增压效果的压缩机，由于压缩机从气液分离器内周期性的吸气，使得制冷剂在气液分离器的制冷剂形成周期性的脉动，并且当制冷剂的脉动频率达到吸气共振频率时，制冷剂在气液分离器内的脉动幅度达到最大，该类型压缩机的吸气频率与吸气共振频率相当(压缩机的吸气频率一般不大于吸气共振频率)，制冷剂共振产生的压力波对压缩机的吸气产生抽吸增压效果，进而使吸入压缩机的制冷剂的量变多，使压缩机的压缩性能增强。
公开号为CN107002655A的专利申请，记载了能够获得该抽吸增压效果的压缩机的共振峰值转速(吸气共振频率)的计算公式，也即制冷剂的一阶共振频率f可由公式f＝C/{4[L+(V/A)]}求出。式中，C为声音在制冷剂中传播的速度(m/s)，L为制冷剂流动的出口管的长度(m)，V为压缩机的排量(m 3)，A为出口管的截面积(m 2)。
然而，现有的压缩机向着压缩频率越来越高的方向发展，也即压缩机的吸气频率越来越高，这就导致压缩机的吸气频率超出吸气共振频率，致使压缩机在吸气时不能利用制冷剂的共振脉动来达到抽吸增压的效果，压缩机的吸气量减少，导致压缩机的性能恶化。
从制冷剂的一阶共振频率f的公式可以看出，可以通过减小出口管长度L、减小压缩机排量V或是增大出口管截面积A的方式来增大制冷剂的一阶共振频率f，其中压缩机排量V和出口管截面积A变化对制冷剂的一阶共振频率f的影响较小，出口管长度L对制冷剂的一阶共振频率f的影响较大。
然而，由于出口管一般从气液分离器的底部穿出，减短出口管的长度也就意味着同时要减短气液分离器的长度，减小气液分离器的容量，而这就意味着需要减弱气液分离器的功能，致使压缩机受到液击的可能性加大，影响压缩机的性能。
对此，公开号为CN205349734U的专利，记载了一种出口管从气液分离器的壳体侧壁穿出至壳体之外的技术方案，这样能够实现只减短出口管的长度，而不减短气液分离器的长度出口管L，不影响气液分离器的容量，然而，这样容易使气液分离器的位于出口管以下的区域出现积油问题，使压缩机内润滑油减少，从而影响压缩机长期运行的可靠性；另外，由于出口管从气液分离器的壳体侧壁穿出至壳体之外，出口管的大部分悬空伸至气液分离器的内腔中，这就使得出口管在压缩机运行时容易产生较大的振动，容易导致噪声增大，甚至可能造成出口管损坏和断裂。
发明内容
本申请的主要目的是提供一种便于提升高频压缩性能且方便润滑油回流的气液分离器。
为了实现上述的主要目的，本申请提供的气液分离器包括壳体、出口管和吸液管，出口管伸于气液分离器的内腔中并从壳体的侧壁穿出至壳体外，吸液管的一端伸至气液分离器的内腔底部，吸液管的另一端与出口管连接。
由上可见，本申请通过对气液分离器的设置和结构设计，由于出口管从气液分离器的壳体的侧壁穿出至壳体外，这样一方面有利于减短出口管的长度，有利于提升制冷剂的一阶共振频率，避免压缩机高频运行时的吸气频率明显超出制冷剂的一阶共振频率，使气液分离器内腔中制冷剂的一阶共振频率能够与高频压缩机的吸气频率相当，便于压缩机在高频运行时产生抽吸增压效果，以增强压缩机的进气效率，增强压缩机的性能；此外，吸液管的设置便于将气液分离器底部的润滑油吸入压缩机，避免大量润滑油在气液分离器的内腔底部积聚，使压缩机持续得到润滑，保证压缩机长期可靠运行。
一个优选的方案是，出口管具有内伸段和外接段，内伸段位于气液分离器的内腔中，外接段从壳体的侧壁穿出至壳体外，吸液管与外接段连接。
进一步的方案是，内伸段沿竖直方向延伸。
进一步的方案是，外接段沿水平方向延伸。
另一个优选的方案是，出口管具有两根，至少一根出口管从壳体的侧壁穿出至壳体外。
进一步的方案是，两根出口管均从壳体的侧壁穿出至壳体外。
再一个优选的方案是，出口管从壳体的侧壁的第一位置穿出至壳体外，第一位置与壳体底端的距离不大于第一位置与壳体顶端的距离。
由上可见，这样有利于减弱气液分离器的下端部的振动，降低气液分离器的振动噪声。
又一个优选的方案是，气液分离器还包括固定件，固定件位于气液分离器的内腔中，固定件固定连接壳体与出口管。
由上可见，这样有利于降低出口管的振动强度。
进一步的方案是，出口管从壳体的侧壁的第一位置穿出至壳体外，出口管与固定件连接于第二位置，沿竖直方向，第一位置与第二位置相距第一距离，出口管的伸至气液分离器的内腔顶部的一端与第一位置相距第二距离，第一距离与第二距离的比值为0.3至0.7。
由上可见，这样有利于平衡出口管各处的振动强度，避免出口管局部振动剧烈，避免出口管局部因振动而损坏。
还一个优选的方案是，吸液管的截面积明显小于出口管的截面积。
由上可见，这样能够避免大量液体流入压缩机，避免对压缩机造成液击，此外也使压缩机得能够长期通过吸液管吸入润滑油，有利于保证压缩机长期可靠运行。
本申请的另一目的是提供一种便于提升高频压缩性能且方便润滑油回流的气液分离器。
为了实现上述的另一目的，本申请提供的压缩机组件包括压缩机和气液分离器，气液分离器包括壳体、出口管和吸液管，出口管伸至气液分离器的内腔中，出口管从壳体的侧壁穿出至壳体外，吸液管的一端伸至气液分离器的内腔底部，吸液管的另一端与压缩机的流体入口连通。
由上可见，本申请通过对压缩机组件的设置和结构设计，由于出口管从壳体的侧壁穿出至壳体外，这样一方面有利于减短出口管的长度，有利于提升制冷剂的一阶共振频率，避免压缩机高频运行时的吸气频率明显超出制冷剂的一阶共振频率，便于压缩机在高频运行时能够有效利用抽吸增压效果，以增强压缩机的进气效率，增强压缩机的性能；此外，吸液管的设置便于将气液分离器底部的润滑油吸入压缩机，避免大量润滑油在气液分离器的内腔底部积聚，使压缩机持续得到润滑，保证压缩机长期可靠运行。
本申请的再一目的是提供一种压缩机高频压缩性能良好且润滑油回液方便的压缩机组件。
为了实现上述的再一目的，本申请提供的压缩机组件包括压缩机和前述的气液分离器，出口管的穿出壳体之外的一端与压缩机连接。
由上可见，本申请的压缩机组件由于采用前述的气液分离器，使得压缩机在高频运行时的吸气效率得到提升，有利于提升压缩机的高频运行性能，此外，也有利于保证压缩机长期可靠运行。
本申请的又一目的是提供一种压缩机高频压缩性能良好且润滑油回液方便的压缩机组件。
为了实现上述的又一目的，本申请提供的压缩机组件，包括压缩机、连接件和前述的气液分离器，出口管在穿出壳体的位置与壳体固定连接，出口管的穿出壳体之外的一端与压缩机固定连接，连接件固定连接于压缩机的机壳与壳体之间；沿竖直方向，出口管固定连接于壳体的第一高度位置，固定件固定连接于壳体的第二高度位置，连接件固定连接于壳体的第三高度位置，第二高度位置位于第一高度位置与第三高度位置之间。
由上可见，本申请的压缩机组件由于采用前述的气液分离器，使得压缩机在高频运行时的吸气效率得到提升，有利于提升压缩机的高频运行性能，也有利于保证压缩机长期可靠运行；此外，将第二高度位置设于第一高度位置与第三高度位置之间，这样内伸段的振动通过固定件传递给筒体的第一高度位置和第三高度位置之间，有利于增强内伸段的连接刚度，降低内伸段的振动强度，降低气液分离器的振动强度。
本申请的再一目的是提供一种压缩机高频压缩性能良好且润滑油回液方便的空调器。
为了实现上述的再一目的，本申请提供的空调器包括前述的压缩机组件。
由上可见，本申请的压缩机组件由于采用前述的压缩机，使得压缩机在高频运行时的吸气效率得到提升，有利于提升压缩机的高频运行性能，有利于提升空调器的高频性能，此外，也有利于保证压缩机长期可靠运行，有利于空调器长期可靠的运行。
附图说明
图1是现有技术案例的气液分离器剖视图；
图2是现有技术案例的压缩机组件剖视图；
图3是本申请气液分离器实施例一的剖视图；
图4是本申请压缩机组件实施例一的剖视图；
图5是本申请气液分离器实施例二的剖视图；
图6是本申请气液分离器实施例三的剖视图；
图7是本申请气液分离器中底壳振动情况随H1/H0比值变化的曲线图；
图8是本申请气液分离器中第一出口管振动情况随H3/H2比值变化的曲线图。
以下结合附图及实施例对本申请作进一步说明。
具体实施方式
气液分离器、压缩机组件及空调器实施例一：
请参照图3至图4，本实施例的空调器安装有本实施例的压缩机组件，本实施例的压缩机组件包括压缩机200和本实施例的气液分离器100，本实施例的气液分离器100包括壳体、第一出口管103和吸液管104，壳体包括筒体101和底壳105，底壳105固定于筒体101的底部，第一出口管103具有沿竖直方向延伸的内伸段131和沿水平方向延伸的外接段133，内伸段131与外接段133之间采用弯曲段132连接，内伸段131及弯曲段132均位于气液分离器100的内腔中，内伸段131伸至气液分离器100内腔的顶部，外接段133从筒体101的侧壁穿出至壳体外，外接段133与压缩机200的机壳通过焊接固定，外接段133与筒体101通过焊接固定，吸液管104的一端伸至气液分离器100的内腔底部，吸液管104的另一端与外接段133连接。
由于外接段133从筒体101的侧壁穿出至壳体外，内伸段131伸至气液分离器100的内腔中，导致内伸段131失去了与筒体101的固定连接，造成内伸段131缺乏固接定位，致使内伸段131可能因振动而断裂损坏，因此在筒体101上固定连接固定件102，固定件102位于气液分离器100的内腔中，固定件102与第一出口管103的内伸部固定连接。
由于外接段133从筒体101的侧壁穿出至壳体外，这样一方面有利于减短第一出口管103的长度，有利于提升气液分离器100内腔中制冷剂的一阶共振频率，避免压缩机高频运行时的吸气频率明显超出制冷剂的一阶共振频率，便于压缩机在高频运行时能够有效利用抽吸增压效果，以增强压缩机的进气效率，增强压缩机的性能；此外，吸液管104的设置便于将气液分离器100内腔底部的润滑油吸入压缩机，避免大量润滑油在气液分离器100的内腔底部积聚，使压缩机持续得到润滑，保证压缩机长期可靠运行。
具体地，请参照图4，筒体101与压缩机200的机壳之间还通过连接件500进行固定，筒体101及压缩机200的机壳均与连接件500焊接，沿竖直方向，连接件500位于外接段133的上方，这样筒体101与压缩机200的机壳之间具有两处固定连接，有利于使气液分离器100与压缩机100的固定连接更加稳定可靠。
沿竖直方向，外接段133固定连接于筒体101的第一高度位置，固定件102固定连接于筒体101的第二高度位置，连接件500固定连接于筒体101的第三高度位置，由于筒体101的第一高度位置及第三高度位置均与压缩机200的机壳固定连接，使得筒体101的介 于第一高度位置与第三高度位置之间的区域具有更好的抗振性能，因此，将第二高度位置设于第一高度位置与第三高度位置之间，这样内伸段131的振动通过固定件102传递给筒体101的第一高度位置和第三高度位置之间，有利于增强内伸段131的连接刚度，降低内伸段131的振动强度，降低气液分离器100的振动强度。
可选择地，连接件500与筒体101除了可以焊接固定之外，还可以通过卡箍、螺钉等一种或多种方式进行固定连接，同理，连接件500与压缩机200的机壳也可以通过卡箍、螺钉等一种或多种方式进行固定连接。
可选择地，吸液管104除了可以与外接段133连接外，还可以直接与压缩机的流体入口连接，吸液管104与第一出口管103各自运行。
优选地，内伸段131与外接段133通过弯曲段132连接，这样有利于避免应力在内伸段131与外接段133的连接处集中，提升第一出口管103的抗振性能。
具体地，压缩机200为双缸压缩机，气液分离器100还具有第二出口管，第一出口管103及第二出口管106各自具有沿竖直方向延伸的内伸段131和沿水平方向延伸的外接段133。
优选地，第一出口管103及第二出口管106均为圆管。
请参照图3，设气液分离器100的壳体总高度为H0，第一出口管103的外接段133的管轴线与底壳105底部的距离为H1，第一出口管103的外接段133的管轴线与内伸段131的顶端的距离为H2，第一出口管103的外接段133的管轴线与固定件102的距离为H3。
第二出口管106的顶端与第一出口管103的顶端平齐，第二出口管106的外接段133位于第一出口管103的外接管下方，第二出口管106的外接段133的管轴线与第一出口管103的外接段133的管轴线相距H4。
由于外接段133从筒体101的侧壁穿出至壳体外，外接段133在穿出位置与筒体101固定，外接段133不再与气液分离器100的底壳105固定，气液分离器100的底壳105容易发生较大振动，为了降低气液分离器100底壳105的振动强度，本实施例在H1/H0介于0.2至0.7范围内不同情况下，在Ansys仿真软件上仿真气液分离器100的底壳105的最大振动值，并以H1/H0＝0.5时气液分离器100的底壳105的最大振动值为参考(取H1/H0＝0.5时气液分离器100的底壳105的最大振动值b的相对值为1，用H1/H0取其它值时气液分离器100的底壳105的最大振动值a除以H1/H0＝0.5时气液分离器100的底壳105的最大振动值b得到a/b，a/b的值为H1/H0取对应值时气液分离器100的底壳105的相对振动 值)，作H1/H0介于0.2至0.7范围内不同情况下气液分离器100的底壳105的相对振动值曲线图如图7所示。
如图7所示，H1/H0＝0.4时气液分离器100的底壳105的振动最弱，当H1/H0大于0.5以后气液分离器100的底壳105的振动急剧增强，因此限制H1/H0不大于0.5，并且随着H1/H0的值减小，第一出口管103长度L1的值将随之增大，因此，更优选地，限制H1/H0为介于0.4至0.5之间，这样能够尽可能的平衡第一出口管103长度L1与气液分离器100的底壳105的振动强度之间的关系，既有利于压缩机利用吸气增压，提升压缩机性能，又尽可能降低气液分离器100的振动，降低压缩机运行的噪声。
第一出口管103上越远离固定位置的位置振动越剧烈，为了确定固定件102的最优位置，本实施例在Ansys仿真软件上仿真内伸段131顶端和弯曲段132在H3/H2介于0.1至0.9范围内不同情况下的最大振动值，并以H3/H2＝0.7时内伸段131顶端的最大振动值为参考(取H3/H2＝0.7时内伸段131顶端的最大振动值d的相对值为1，H3/H2为其它值时的内伸段131顶端或弯曲段132的最大振动值为c，则c/d为该H3/H2情况下的内伸段131顶端或弯曲段132的相对振动值)，作H3/H2介于0.1至0.9范围内不同情况下内伸段131顶端和弯曲段132的相对振动值曲线图如图8所示。
如图8所示，随着H3/H2比值的增加，内伸段131顶端的相对振动值不断降低，且在H3/H2小于0.3的区间内，内伸段131顶端的相对振动值降低速率较快；随着H3/H2比值的增加，弯曲段132的振动值不断增大，且在H3/H2大于0.7后弯曲段132的振动增强较快；因此取H3/H2介于0.3至0.7之间这样既避免内伸段131顶端振动急剧增强，也避免弯曲段132的振动急剧增强。
本实施例中，气液分离器100及压缩机200的各参数如下：H0＝235mm，H1＝80mm，H2＝120mm，H3＝47mm,H4＝32mm，单个管道的截面积A1＝201mm 2,第一出口管103的长度L1＝188mm,第二出口管106的长度L2＝252mm，单个压缩缸的排量V1＝22cm 3，声音在制冷剂中的传播速率C＝228m/s。按第一出口管103的各参数计算吸气共振频率f1＝228/{4[0.188+22/201]}＝192s -1，按照第二出口管106的参数计算气液分离器100中吸气共振频率f2＝228/{4[0.252+22/201]}＝158s -1。因此，气液分离器100中吸气共振频率应介于158s -1与192s -1之间，气液分离器100中吸气共振频率约为(192+158)/2＝175s -1。
请参照图1及图2，现有技术的双缸压缩机中，气液分离器300包括第三出口管303和第四出口管306，第三出口管303与第四出口管306均从气液分离器300的底壳穿出至壳体外，然后与压缩机400的机壳固定连接，设气液分离器300的壳体总高度为H5，第三 出口管303的外接段333的管轴线与底壳底部的距离为H6，第三出口管303的外接段333的管轴线与内伸段331的顶端的距离为H7，第三出口管303的外接段333的管轴线与固定件102的距离为H8。
第四出口管306的顶端与第三出口管303的顶端平齐，第四出口管306的外接段位于第三出口管303的外接段333下方，第四出口管306的外接段的管轴线与第三出口管303的外接段333的管轴线相距H9。
现有技术中，气液分离器300及压缩机的各参数如下：H5＝180mm，H6＝55.5mm，H7＝200mm，H8＝152mm,H9＝32mm，单个管道的截面积A2＝201mm 2,第三出口管303的长度L3＝268mm,第四出口管306的长度L4＝332，单个压缩缸的排量V2＝22cm 3，声音在制冷剂中的传播速率C＝228m/s。按第三出口管303的各参数计算吸气共振频率f3＝228/{4[0.268+22/201]}＝151s -1，按照第四出口管306的参数计算气液分离器300中吸气共振频率f4＝228/{4[0.332+22/201]}＝129s -1。因此，气液分离器300中吸气共振频率应介于129s -1与151s -1之间，气液分离器300中吸气共振频率约为(129+151)/2＝140s -1。
若此时压缩机以吸气频率为180Hz进行运转，通过检测可以得到如下数据：
  本实施例方案 现有技术案例
气液分离器有效容积(cc) 860 640
吸气共振频率f(s -1) 介于158至192之间 介于129至151之间
压缩机容积效率(％) 114.7 93.2
气液分离器100振动(m/s 2) 24.1 37.7
噪声(dB) 78.3 81.5
由上表可以看出，本实施例技术方案相较于现有技术案例的方案而言，本技术方案实施例的气液分离器100的有效容积明显大于现有技术案例气液分离器300的有效容积，压缩机的容积效率得到明显提升，本实施例技术方案气液分离器100的振动和噪声相较于现有技术案例的气液分离器300都明显减弱。
气液分离器、压缩机组件及空调器实施例二：
如图5所示，第一出口管103从筒体101的侧壁穿出至壳体外，第二出口管106从底壳105穿出至壳体外，这样也能一定程度上缩短第一出口管103及第二出口管103的长度，提升气液分离器100内腔中吸气共振频率。
气液分离器、压缩机组件及空调器实施例二的其余部分同气液分离器、压缩机组件及空调器实施例一。
气液分离器、压缩机组件及空调器实施例三：
如图6所示，本实施例中，气液分离器100只有第一出口管103，本实施例的气液分离器100用于单缸压缩机。
气液分离器、压缩机组件及空调器实施例三的其余部分同气液分离器、压缩机组件及空调器实施例一。
最后需要强调的是，以上所述仅为本申请的优选实施例，并不用于限制本申请，对于本领域的技术人员来说，本申请可以有各种变化和更改，凡在本申请的精神和原则之内，所做的任何修改、等同替换、改进等，均应包含在本申请的保护范围之内。

Claims (13)

  1. 一种气液分离器，包括壳体和出口管，其特征在于：
    所述出口管伸于所述气液分离器的内腔中并从所述壳体的侧壁穿出至所述壳体外，所述气液分离器还包括吸液管，所述吸液管的一端伸至所述气液分离器的内腔底部，所述吸液管的另一端与所述出口管连接。
  2. 根据权利要求1所述的气液分离器，其特征在于：
    所述出口管具有内伸段和外接段，所述内伸段位于所述气液分离器的内腔中，所述外接段从所述壳体的侧壁穿出至所述壳体外，所述吸液管与所述外接段连接。
  3. 根据权利要求2所述的气液分离器，其特征在于：
    所述内伸段沿竖直方向延伸。
  4. 根据权利要求2所述的气液分离器，其特征在于：
    所述外接段沿水平方向延伸。
  5. 根据权利要求1至4任一项所述的气液分离器，其特征在于：
    所述出口管具有两根，至少一根所述出口管从所述壳体的侧壁穿出至所述壳体外。
  6. 根据权利要求5所述的气液分离器，其特征在于：
    两根所述出口管均从所述壳体的侧壁穿出至所述壳体外。
  7. 根据权利要求1至4任一项所述的气液分离器，其特征在于：
    所述出口管从所述壳体的侧壁的第一位置穿出至所述壳体外，所述第一位置与所述壳体底端的距离不大于所述第一位置与所述壳体顶端的距离。
  8. 根据权利要求1至4任一项所述的气液分离器，其特征在于：
    所述气液分离器还包括固定件，所述固定件位于所述气液分离器的内腔中，所述固定件固定连接所述壳体与所述出口管。
  9. 根据权利要求8所述的气液分离器，其特征在于：
    所述出口管从所述壳体的侧壁的第一位置穿出至所述壳体外，所述出口管与所述固定件连接于第二位置，沿竖直方向，所述第一位置与所述第二位置相距第一距离，所述出口管的伸至所述气液分离器的内腔顶部的一端与所述第一位置相距第二距离，所述第一距离与所述第二距离的比值为0.3至0.7。
  10. 一种压缩机组件，包括压缩机，其特征在于：
    还包括气液分离器，包括壳体、出口管和吸液管，所述出口管伸至所述气液分离器的内腔中，所述出口管从所述壳体的侧壁穿出至所述壳体外，所述吸液管的一端伸至所述气液分离器的内腔底部，所述吸液管的另一端与所述压缩机的流体入口连通。
  11. 一种压缩机组件，包括压缩机，其特征在于：
    还包括如权利要求1至7任一项所述的气液分离器，所述出口管的穿出所述壳体之外的一端与所述压缩机连接。
  12. 一种压缩机组件，包括压缩机，其特征在于：
    还包括连接件和如权利要求8或9所述的气液分离器，所述出口管在穿出所述壳体的位置与所述壳体固定连接，所述出口管的穿出所述壳体之外的一端与所述压缩机固定连接，所述连接件固定连接于所述压缩机的机壳与所述壳体之间；
    沿竖直方向，所述出口管固定连接于所述壳体的第一高度位置，所述固定件固定连接于所述壳体的第二高度位置，所述连接件固定连接于所述壳体的第三高度位置，所述第二高度位置位于所述第一高度位置与所述第三高度位置之间。
  13. 一种空调器，其特征在于：
    包括如权利要求11所述的压缩机组件。
PCT/CN2019/110745 2019-03-13 2019-10-12 气液分离器、压缩机组件及空调器 WO2020181764A1 (zh)

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