EP4520974A1 - Elektrischer verdichter, klimaanlage und fahrzeug - Google Patents

Elektrischer verdichter, klimaanlage und fahrzeug Download PDF

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Publication number
EP4520974A1
EP4520974A1 EP23825854.5A EP23825854A EP4520974A1 EP 4520974 A1 EP4520974 A1 EP 4520974A1 EP 23825854 A EP23825854 A EP 23825854A EP 4520974 A1 EP4520974 A1 EP 4520974A1
Authority
EP
European Patent Office
Prior art keywords
communication
silencing cavity
housing
compression mechanism
electric compressor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP23825854.5A
Other languages
English (en)
French (fr)
Other versions
EP4520974A4 (de
Inventor
Jiahui Wu
Luying WANG
Kaicheng YANG
Fayun LI
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Guangdong Welling Auto Parts Co Ltd
Anhui Welling Auto Parts Co Ltd
Original Assignee
Guangdong Welling Auto Parts Co Ltd
Anhui Welling Auto Parts Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from CN202210715848.7A external-priority patent/CN117307489B/zh
Priority claimed from CN202221588958.3U external-priority patent/CN218325275U/zh
Application filed by Guangdong Welling Auto Parts Co Ltd, Anhui Welling Auto Parts Co Ltd filed Critical Guangdong Welling Auto Parts Co Ltd
Publication of EP4520974A1 publication Critical patent/EP4520974A1/de
Publication of EP4520974A4 publication Critical patent/EP4520974A4/de
Pending legal-status Critical Current

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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
    • F04C29/06—Silencing
    • F04C29/065—Noise dampening volumes, e.g. muffler chambers
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/06—Silencing
    • F04C29/068—Silencing the silencing means being arranged inside the pump housing
    • 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
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • 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
    • F04C18/356—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 outer member
    • 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

Definitions

  • the present disclosure relates to the field of compressor technologies, and more particularly, to an electric compressor, an air conditioning system, and a vehicle.
  • An electric compressor is a core component of a refrigeration device for a vehicle.
  • the electric compressor generates vibration noise during its operation, which would affect vehicle noise and causes a subjective hearing issue.
  • a high-pressure refrigerant discharged from a compression mechanism of the electric compressor exits the electric compressor from a refrigerant discharge outlet after being subjected to a gas-liquid separation in an oil separation chamber.
  • Exhaust airflow noise and pressure pulsations generated during the operation of the electric compressor are likely to stimulate resonance of various components of a thermal management system of the vehicle, which brings about problems of noise and vibration of the vehicle.
  • inventions of the present disclosure aims to solve at least one of the technical problems in the related art.
  • embodiments of the present disclosure provide an electric compressor, which can mitigate noise and vibration generated during an operation of the electric compressor.
  • Embodiments of the present disclosure further provide an air conditioning system having the electric compressor as described above.
  • Embodiments of the present disclosure further provide a vehicle having air conditioning system as described above.
  • an electric compressor includes a housing assembly and a compression mechanism.
  • the housing assembly includes a first housing and a support, and two axial ends of the first housing are a first end and a second end, respectively.
  • the support is disposed at the first end of the first housing to form an accommodation chamber between the support and the first housing.
  • the first housing has an oil separation chamber and a refrigerant discharge outlet.
  • the oil separation chamber is located closer to the second end than the first end, and the oil separation chamber has an oil separation outlet in communication with the refrigerant discharge outlet.
  • the compression mechanism is disposed in the accommodation chamber.
  • a first silencing cavity is formed between the compression mechanism and the support.
  • the compression mechanism has a first exhaust outlet in communication with the first silencing cavity, and the first silencing cavity is in communication with an oil separation inlet of the oil separation chamber.
  • the second end of the first housing is closed, and the oil separation chamber is formed in an end housing part of the first housing at the second end.
  • a first communication passage is formed in a side housing part of the first housing.
  • the first silencing cavity and the oil separation inlet of the oil separation chamber are in communication with each other through the first communication passage.
  • a first communication hole is formed at a connection between the first housing and the support, and the first communication passage is in communication with the first silencing cavity through the first communication hole.
  • the first communication hole has a smaller flow area than the first communication passage.
  • the first communication hole is formed at the support or at the first housing, or the first communication hole is defined by an insertion tube inserted into the first housing or the support.
  • the first communication hole has a minimum flow area of S1
  • the first silencing cavity has a volume of V1, where 0.06 ⁇ S1/V1 ⁇ 2.0.
  • the compression mechanism has a second silencing cavity in communication with the first silencing cavity.
  • the second silencing cavity is spaced apart from the first silencing cavity in an axial direction of the compression mechanism.
  • a second communication passage is formed at the compression mechanism. The second silencing cavity and the first silencing cavity are in communication with each other through the second communication passage.
  • the second communication passage has a minimum flow area of S2; and the second silencing cavity has a volume of V2, where 0.08 ⁇ S2/V2 ⁇ 2.2.
  • a high-pressure cavity is formed between a wall of the accommodation chamber and the compression mechanism, and the first silencing cavity and the oil separation inlet of the oil separation chamber are in communication with each other through the high-pressure cavity.
  • the compression mechanism is a rotary compression mechanism or a scroll compression mechanism.
  • an air conditioning system includes the electric compressor according to any of the embodiments in the first aspect.
  • a vehicle in a third aspect of the present disclosure, includes a vehicle body and the air conditioning system in the second aspect of the present disclosure.
  • the air conditioning system is mounted at the vehicle body.
  • electric compressor 100 housing assembly 1; accommodation chamber 10; first silencing cavity 101; high-pressure cavity 102; first housing 11; first end 111; second end 112; oil separation chamber 113 oil separation outlet 1131; oil separation inlet 1132; exhaust tube 1133; refrigerant discharge outlet 114; first communication passage 115; support 12; gasket 13; compression mechanism 2; first exhaust outlet 21; second silencing cavity 22; second communication passage 23; second communication hole 24; first cylinder 251; second cylinder 252; first piston 261; second piston 262; partition 27; first bearing 281; second bearing 282; second exhaust outlet 283; silencer 29; first communication hole 3; drive shaft 4; air conditioning system 200; vehicle 300.
  • an electric compressor 100 includes a housing assembly 1 and a compression mechanism 2.
  • the compression mechanism 2 is configured to compress a low-pressure refrigerant into a high-pressure refrigerant.
  • the housing assembly 1 includes a first housing 11 and a support 12. Two axial ends of the first housing 11 are a first end 111 and a second end 112, respectively.
  • the support 12 is disposed at the first end 111 of the first housing 11 to form an accommodation chamber 10 between the support 12 and the first housing 11.
  • the first housing 11 has an oil separation chamber 113 and a refrigerant discharge outlet 114. That is, both the oil separation chamber 113 and the refrigerant discharge outlet 114 are integrally formed on the first housing 11.
  • the compression mechanism 2 is disposed in the accommodation chamber 10.
  • a first silencing cavity 101 is formed between the compression mechanism 2 and the support 12.
  • the compression mechanism 2 has a first exhaust outlet 21 in communication with the first silencing cavity 101.
  • the first silencing cavity 101 is in communication with an oil separation inlet 1132 of the oil separation chamber 113.
  • An oil separation outlet 1131 of the oil separation chamber 113 is in communication with the refrigerant discharge outlet 114.
  • the oil separation chamber 113 is configured to separate a gas and a liquid in the high-pressure refrigerant from each other, and then the gas is discharged through the refrigerant discharge outlet 114.
  • the low-pressure refrigerant may be sucked, and then compressed into the high-pressure refrigerant by the compression mechanism 2.
  • the high-pressure refrigerant is then discharged into the first silencing cavity 101 through the first exhaust outlet 21 of the compression mechanism 2.
  • the high-pressure refrigerant in the first silencing cavity 101 enters the oil separation chamber 113 through the oil separation inlet 1132 to undergo a gas-liquid separation.
  • the separated gaseous refrigerant is finally discharged out of the housing assembly 1 through the refrigerant discharge outlet 114.
  • the oil separation chamber 113 is located closer to the second end 112 than the first end 111. That is, an axial distance between the oil separation chamber 113 and the second end 112 is smaller than that between the oil separation chamber 113 and the first end 111. Since the first silencing cavity 101 is formed by the compression mechanism 2 and the support 12 together, and the support 12 is located at the first end 111 of the first housing 11, the first silencing cavity 101 is closer to the first end 111 than the second end 112. That is, an axial distance between the first silencing cavity 101 and the first end 111 is smaller than that between the first silencing cavity 101 and the second end 112. Therefore, at the first housing 11, the first silencing cavity 101 is spaced apart from the oil separation chamber 113 by a predetermined axial distance. It should be noted that an axial direction of the first housing 11 is same as that of the compression mechanism 2.
  • the oil separation chamber 113 is at a predetermined distance from the first silencing cavity 101, which can increase a flow distance of the high-pressure refrigerant flowing from the first silencing cavity 101 to the oil separation chamber 113, thereby mitigating flow noise and pressure pulsations of the high-pressure refrigerant. Therefore, operation noise and vibration of the electric compressor 100 can be mitigated.
  • the electric compressor 100 has a relatively compact overall structure, which is conducive to reducing a volume of and a space occupied by the electric compressor 100, improving versatility of the electric compressor 100.
  • compactness of the electric compressor 100 can be further improved. In this way, a space in the electric compressor 100 can be efficiently utilized while the volume of the electric compressor 100 is limited, allowing the volume of and the space occupied by the electric compressor 100 to be further reduced.
  • the electric compressor is subjected to strict control on its size and weight to ensure optimal key performance such as a vehicle range.
  • the compressor has a limited internal volume. Therefore, after space requirements for a compression component and a motor component are satisfied, a volume of a cavity available for refrigerant buffering and noise elimination is small.
  • An exhaust solution provided in the present disclosure can provide an effective solution on how to utilize a limited volume to enhance a noise reduction effect.
  • the second end 112 of the first housing 11 is closed.
  • the oil separation chamber 113 is formed in an end housing part of the first housing 11 at the second end 112.
  • the oil separation chamber 113 and the first silencing cavity 101 are located at the second end 112 of the first housing 11 and the first end 111 of the first housing 11, respectively.
  • a distance between the oil separation chamber 113 and the first silencing cavity 101 is relatively great, which can increase the flow distance of the high-pressure refrigerant flowing from the first silencing cavity 101 to the oil separation chamber 113, thereby better mitigating the flow noise and the pressure pulsations of the high-pressure refrigerant. Therefore, the operation noise and the vibration of the electric compressor 100 are further mitigated.
  • the second end 112 of the first housing 11 in a closed form, a structure of the housing assembly 1 can be simplified, saving a cost and steps of closing the second end 112 by using other components.
  • the oil separation chamber 113 in the end housing part of the first housing 11 at the second end 112, the oil separation chamber 113 can be prevented from occupying too much space of the accommodation chamber 10 to ensure a sufficient available volume of the accommodation chamber 10.
  • problems such as interference between the oil separation chamber 113 and the compression mechanism 2 in the accommodation chamber 10 can be avoided, improving generality.
  • a first communication passage 115 is formed in a side housing part of the first housing 11.
  • the first silencing cavity 101 and the oil separation inlet 1132 of the oil separation chamber 113 are in communication with each other through the first communication passage 115. Therefore, the high-pressure refrigerant in the first silencing cavity 101 flows into the first communication passage 115, and then flows into the oil separation chamber 113 through the oil separation inlet 1132. In this way, an exhaust efficiency can be improved.
  • the first silencing cavity 101 can be prevented from exhausting a gas towards the accommodation chamber 10 in a case where the accommodation chamber 10 has an oil pool, to avoid other adverse effects due to an unstable liquid level of the oil pool.
  • the first communication passage 115 is formed at the inner side of of the first housing 11. Therefore, the first communication passage 115 is prevented from occupying the space of the accommodation chamber 10. Further, the first communication passage 115 has relatively high structural strength, which allows the first communication passage 115 to be less likely to be deformed under a pressure of the high-pressure refrigerant, improving reliability of the electric compressor 100.
  • a method for forming the first communication passage 115 at the first housing 11 is not limited.
  • the first communication passage 115 may be formed directly during casting or injection molding of the first housing 11.
  • the first communication passage 115 may be formed by punching a hole in the first housing 11.
  • the first communication passage 115 may extend along a straight line, a curve, or the like, and the present disclosure is not limited in this regard.
  • the number of the first communication passage 115 is not limited in the present disclosure.
  • One first communication passage 115 may be formed, or a plurality of first communication passages 115 independently enabling the first silencing cavity 101 to be in communication with the oil separation chamber 113 may be formed. It should be noted that when the plurality of first communication passages 115 is formed, a total flow area of the plurality of first communication passages 115 can be set to be equal to a flow area of one first communication passage 115.
  • a first communication hole 3 is formed at a connection between the first housing 11 and the support 12.
  • the first communication passage 115 is in communication with the first silencing cavity 101 through the first communication hole 3.
  • the first communication hole 3 has a smaller flow area than the first communication passage 115. Therefore, since a refrigerant path from the first silencing cavity 101 to the oil separation chamber 113 has a variable flow area, the first communication passage 115 of a relatively great flow area may be used to ensure the exhaust efficiency, while the first communication hole 3 of a relatively small flow area may be used for a design of relevant dimensions to enhance the noise reduction effect.
  • the flow area decreases and then increases, which is more conducive to mitigating the flow noise and the pressure pulsations of the high-pressure refrigerant in the first housing 11, further mitigating the operation noise and the vibration of the electric compressor 100.
  • a position and a shape of the first communication hole 3 are not limited in the present disclosure.
  • the first communication hole 3 may be formed at the support 12 or at the first housing 11, or the first communication hole 3 may be defined by an insertion tube inserted into the first housing 11 or the support 12. Therefore, the position of the first communication hole 3 is flexible.
  • the first communication hole 3 may be formed at the support 12 or at the first housing 11, or may be formed as a separate structure.
  • the first communication hole 3 is formed at the support 12.
  • a passageway is formed at a connection between the support 12 and the first communication passage 115, and the passageway has a smaller flow area than the first communication passage 115.
  • the passageway serves as the first communication hole 3.
  • the first communication hole 3 is formed at first housing 11.
  • the first communication hole 3 may be formed as a passageway between the first communication passage 115 and the first silencing cavity 101.
  • the first communication hole 3 has a smaller flow area than the first communication passage 115.
  • a gasket 13 is disposed between the first housing 11 and the support 12.
  • the first communication hole 3 may be an insertion tube disposed at the gasket 13 and corresponding to the first communication passage 115.
  • the insertion tube may be inserted into the first communication passage 115, or into the first silencing cavity 101, or into both the first communication passage 115 and the first silencing cavity 101.
  • the first communication hole 3 has a minimum flow area of S1
  • the first silencing cavity 101 has a volume of V1, where 0.06 ⁇ S1/V1 ⁇ 2.0.
  • a value of S1/V1 may be 0.06, 0.1, 0.5, 1, 1.5, 1.9, and 2.0. With such a structure, the noise reduction effect is relatively satisfactory.
  • the number of the first communication holes 3 may be same as that of the first communication passages 115, and thus a plurality of first communication holes 3 is formed. In this case, the plurality of first communication holes 3 has a total flow area of S1.
  • the compression mechanism 2 may further have a second silencing cavity 22 in communication with the first silencing cavity 101. Therefore, the high-pressure refrigerant compressed by the compression mechanism 2 is discharged into the first silencing cavity 101 and the second silencing cavity 22. With the second silencing cavity 22 in communication with the first silencing cavity 101, a total volume of silencing cavities in the electric compressor 100 can be increased.
  • the high-pressure refrigerant is accommodated in a relatively large space after being discharged into the first silencing cavity 101 and the second silencing cavity 22, which lowers the pressure of the high-pressure refrigerant, reducing a pressures exerted on inner walls of the first silencing cavity 101 and the second silencing cavity 22. In this way, the flow noise and the pressure pulsations due to the high-pressure refrigerant can be mitigated.
  • the second silencing cavity 22 is spaced apart from the first silencing cavity 101 in an axial direction of the compression mechanism 2.
  • a second communication passage 23 is formed at the compression mechanism 2.
  • the second silencing cavity 22 and the first silencing cavity 101 are in communication with each other through the second communication passage 23. Therefore, after the high-pressure refrigerant compressed by the compression mechanism 2 is discharged into the first silencing cavity 101, the high-pressure refrigerant enters the second silencing cavity 22 along the second communication passage 23.
  • the high-pressure refrigerant entering the second silencing cavity 22 can flow back into the first silencing cavity 101 through the second communication passage 23. Thereafter, the high-pressure refrigerant enters the oil separation chamber 113 through the oil separation inlet 1132.
  • the separated gaseous refrigerant is finally discharged out of the housing assembly 1 through the refrigerant discharge outlet 114.
  • the second silencing cavity 22 is spaced apart from the first silencing cavity 101 in the axial direction of the compression mechanism 2, a predetermined axial distance is formed between the second silencing cavity 22 and the first silencing cavity 101. Therefore, the high-pressure refrigerant flows in the second communication passage 23 for a predetermined flow distance, which can better mitigate the flow noise and the pressure pulsations of the high-pressure refrigerant, mitigating the operation noise and the vibration of the electric compressor 100.
  • the compression mechanism 2 may further have a second exhaust outlet 283.
  • the second exhaust outlet 283 is configured to directly exhaust the gas towards the second silencing cavity 22, thereby improving the exhaust efficiency.
  • a flow space for the high-pressure refrigerant in the first silencing cavity 101 and the second silencing cavity 22 is greater than the flow area of the second communication passage 23.
  • the number of the second communication passage 23 is not limited in the present disclosure.
  • One second communication passage 23 may be formed, or a plurality of second communication passages 23 independently enabling the first silencing cavity 101 to be in communication with the second silencing cavity 22 may be formed. It should be further noted that when the plurality of second communication passages 23 is formed, a total flow area of the plurality of second communication passages 23 is equal to a flow area of one second communication passage 23.
  • the second communication passage 23 has a minimum flow area of S2, and the second silencing cavity 22 has a volume of V2, where 0.08 ⁇ S2/V2 ⁇ 2.2.
  • a value of S2/V2 may be 0.08, 0.1, 0.5, 1, 1.5, 1.9, and 2.2.
  • the plurality of second communication passages 23 has a total flow area of S2.
  • a distribution ratio of "cavity-tube-cavity-tube" may be controlled based on an inherent topology of a flow passage of the compressor, for example, a ratio of a flow area of the flow passage to a cavity volume, which can alleviate a noise issue of the compressor, especially a low-frequency noise issue.
  • FIG. 9 reveals that, when the vehicle is under an idle condition, the pressure pulsations have a relatively small amplitude within a range of 0.08 ⁇ S2/V2 ⁇ 0.8, and thus optimal attenuation of the fluid pulsations and an optimal silencing effect are achieved.
  • the pressure pulsations When the vehicle is under a low-speed refrigeration condition, the pressure pulsations have a relatively small amplitude within a range of 0.4 ⁇ S2/V2 ⁇ 0.8, and thus the optimal attenuation of the fluid pulsations and the optimal silencing effect are achieved.
  • a range between the above two ranges i.e., a range of 0.08 ⁇ S2/V2 ⁇ 2.2, and thus a relatively satisfactory effect of mitigating the pressure pulsations and the noise is achieved.
  • a high-pressure cavity 102 is formed between a wall of the accommodation chamber 10 and the compression mechanism 2.
  • the first silencing cavity 101 and the oil separation inlet 1132 of the oil separation chamber 113 are in communication with each other through the high-pressure cavity 102. Therefore, the high-pressure refrigerant in the first silencing cavity 101 flows into the high-pressure cavity 102, and then flows into the oil separation chamber 113 through the oil separation inlet 1132.
  • the high-pressure cavity 102 is formed by the wall of the accommodation chamber 10 and the compression mechanism 2 without additionally arranging in the first housing 11 a structure such as a communication tube between the oil separation inlet 1132 and the first silencing cavity 101, which can simplify the structure of the electric compressor 100. Further, no communication passage that enables the oil separation inlet 1132 to be in communication with the first silencing cavity 101 needs to be formed at the first housing 11, which lowers processing difficulty of the first housing 11 and input costs of arranging a communication structure and improves a manufacturing efficiency.
  • the high-pressure cavity 102 has a predetermined space to reduce the pressure of the high-pressure refrigerant flowing in the high-pressure cavity 102, mitigating the pressure pulsations generated by the high-pressure refrigerant.
  • a flow space for the high-pressure refrigerant in the first silencing cavity 101 and the high-pressure cavity 102 may be smaller than a flow space for the high-pressure cavity 102 to mitigate the flow noise and the pressure pulsations of the high-pressure refrigerant in the first housing 11, which can further mitigate the operation noise and the vibration of the electric compressor 100.
  • the compression mechanism 2 has a second communication hole 24 and a second silencing cavity 22 in communication with the first silencing cavity 101.
  • the second silencing cavity 22 and the high-pressure cavity 102 are in communication with each other through the second communication hole 24. Therefore, the high-pressure refrigerant formed by the compression mechanism 2 is discharged into the first silencing cavity 101, and then enters the second silencing cavity 22.
  • the high-pressure refrigerant in the first silencing cavity 101 may flow directly into the high-pressure cavity 102.
  • the high-pressure refrigerant in the second silencing cavity 22 may flow into the high-pressure cavity 102 through the second communication hole 24.
  • the high-pressure refrigerant in the high-pressure cavity 102 flows into the oil separation chamber 113 through the oil separation inlet 1132.
  • the exhaust efficiency can be improved while ensuring the noise reduction effect when the high-pressure refrigerant flows from the second silencing cavity 22 to the high-pressure cavity 102 through the second communication hole 24.
  • the compression mechanism 2 may further have the second exhaust outlet 283.
  • the second exhaust outlet 283 is configured to directly exhaust the gas towards the second silencing cavity 22 to further improve the exhaust efficiency.
  • the first silencing cavity 101 is in communication with the second silencing cavity 22 in such a manner that the high-pressure refrigerant flows between the first silencing cavity 101 and the second silencing cavity 22. In this way, the high-pressure refrigerant in the first silencing cavity 101 and the high-pressure refrigerant in the second silencing cavity 22 have balanced air pressures, which can avoid problems such as vibration of the electric compressor 100 due to a pressure difference between the first silencing cavity 101 and the second silencing cavity 22.
  • the number and a shape of the second communication hole 24 are not limited in the present disclosure.
  • One second communication hole 24 may be formed, or a plurality of second communication holes 24 independently enabling the second silencing cavity 22 to be in communication with the high-pressure cavity 102 may be formed.
  • the oil separation chamber 113 has an oil return hole at a lower part of the oil separation chamber 113.
  • the accommodation chamber 10 may have an oil pool.
  • the oil return hole is in communication with the oil pool to facilitate an oil return.
  • the oil pool is configured to supply a lubricant to the compression mechanism 2. Therefore, structural compactness of the electric compressor 100 can be improved.
  • the oil separation inlet 1132 may extend in a tangential direction of the oil separation chamber 113.
  • the refrigerant entering the oil separation chamber 113 from the oil separation inlet 1132 may flow in a circumferential direction to throw an oil liquid in the refrigerant from the refrigerant by a centrifugal force.
  • the gaseous refrigerant without the oil liquid can be discharged through the oil separation outlet 1131, which generates a satisfactory result of the gas-liquid separation.
  • an exhaust tube 1133 may further be disposed in the oil separation chamber 113.
  • the refrigerant entering the oil separation chamber 113 may flow around the exhaust tube 1133 in a circumferential direction of the exhaust tube 1133 to achieve a more reliable gas-liquid separation.
  • the separated gaseous refrigerant enters the exhaust tube 1133 and is then discharged from the oil separation outlet 1131 through the exhaust tube 1133.
  • a filtration structure such as a filter screen may also be disposed in the oil separation chamber 113 to filter out the oil liquid in the refrigerant.
  • the gaseous refrigerant without the oil liquid may pass through the filtration structure and be discharged through the oil separation outlet 1131. Details thereof will be omitted herein.
  • a type of the compression mechanism 2 is not limited.
  • the compression mechanism 2 may be a rotary compression mechanism or a scroll compression mechanism.
  • compression mechanisms 2 of different types may be applied to different electric compressors 100.
  • the compression mechanism 2 when the electric compressor 100 is a rotary compressor, the compression mechanism 2 is the rotary compression mechanism.
  • the compression mechanism 2 may include a cylinder, a piston, a slider, or the like.
  • a drive shaft 4 of a motor is configured to drive the piston to roll inside the cylinder.
  • the compression mechanism 2 is the scroll compression mechanism.
  • the compression mechanism 2 may include a static scroll disc and a moving scroll disc.
  • the drive shaft is configured to drive the moving scroll disc to rotate.
  • the electric compressor 100 may be a horizontal compressor with a central axis extending in a traverse direction or in a direction slightly inclined to a horizontal line.
  • the electric compressor 100 may be a vertical compressor with a central axis extending in a vertical direction or in a direction slightly inclined to a vertical line, and so on.
  • the compression mechanism 2 when the compression mechanism 2 is the rotary compression mechanism, the compression mechanism 2 may be a single-cylinder compression mechanism or a multi-cylinder compression mechanism.
  • the compression mechanism 2 is a double-cylinder compression mechanism.
  • the compression mechanism 2 includes a first bearing 281, a second bearing 282, a first cylinder 251, a second cylinder 252, a first piston 261, a second piston 262, a partition 27, and a silencer 29.
  • the first cylinder 251 and the second cylinder 252 are axially spaced apart from each other.
  • the first cylinder 251 is located at a side of the second cylinder 252 close to the support 12.
  • the partition 27 is sandwiched between the first cylinder 251 and the second cylinder 252.
  • the first bearing 281 is disposed at a side of the first cylinder 251 away from the partition 27.
  • the second bearing 282 is disposed at a side of the second cylinder 252 away from the partition 27.
  • a first compression cavity is formed between the first cylinder 251, the partition 27, and the first bearing 281.
  • the first piston 261 is rollably adapted to a first compression space.
  • the first bearing 281 has a first exhaust outlet 21 in communication with an exhaust cavity of the first compression space.
  • the first silencing cavity 101 is formed between the first bearing 281 and the support 12.
  • the first exhaust outlet 21 is in communication with the first silencing cavity 101.
  • a second compression cavity is formed between the second cylinder 252, the partition 27, and the second bearing 282.
  • the second piston 262 is rollably adapted to a second compression space.
  • the second bearing 282 has a second exhaust outlet 283 in communication with an exhaust cavity of the second compression space.
  • the silencer 29 is disposed at a side of the second bearing 282 away from the second cylinder 252.
  • the second silencing cavity 22 is formed between the second bearing 282 and the silencer 29.
  • the second exhaust outlet 283 is in communication with the second silencing cavity 22.
  • the silencer 29 has a second communication hole 24.
  • the second silencing cavity 22 and the accommodation chamber 10 are in communication with each other through the second communication hole 24.
  • exemplary application scenarios of the air conditioning system 200 are not limited, and the air conditioning system 200 may be for example applied in an indoor air conditioner, an indoor refrigerator, an in-vehicle air conditioner, or the like.
  • the air conditioning system 200 may further include an evaporator, a condenser, a throttling component, or the like.
  • the air conditioning system 200 when the air conditioning system 200 is applied in the in-vehicle air conditioner, the air conditioning system 200 may further include at least one of an in-vehicle condenser, an in-vehicle evaporator, an out-of-vehicle condenser, an out-of-vehicle evaporator, a throttling component, and the like. Details thereof will be omitted herein.
  • a vehicle 300 includes a vehicle body and the air conditioning system 200 according to any of the above-mentioned embodiments.
  • the air conditioning system 200 is mounted at the vehicle body. Since the exhaust noise and the pressure pulsations of the electric compressor 100 included in the air conditioning system 200 according to any of the above-mentioned embodiments can be mitigated, applying the air conditioning system 200 in the vehicle 300 can ameliorate a problem of resonance of various components in a thermal management system of the vehicle 300 due to exhaust airflow noise and the pressure pulsations of the electric compressor 100, mitigating the noise and the vibration of the vehicle 300.
  • the air conditioning system 200 can be arranged in the vehicle 300 more flexibly.
  • the vehicle 300 may be a new energy vehicle.
  • the new energy vehicle may include a pure electric vehicle, a hybrid vehicle, or the like. Details thereof will be described herein.
  • other components of the vehicle 300 are conceivable for those skilled in the art, and thus details thereof will be omitted herein.
  • the example electric compressor 100 is a rotary electric compressor.
  • the example electric compressor 100 includes the housing assembly 1 and a compression mechanism 2.
  • the compression mechanism 2 is configured to compress a low-pressure refrigerant into a high-pressure refrigerant.
  • the housing assembly includes a first housing 11 and a support 12. Two axial ends of the first housing 11 are a first end 111 and a second end 112, respectively.
  • the support 12 is disposed at the first end 111 of the first housing 11 and engaged with the first housing 11 to form the accommodation chamber 10.
  • the second end 112 of the first housing 11 has an oil separation chamber 113 and a refrigerant discharge outlet 114. Further, an oil separation outlet 1131 of the oil separation chamber 113 is in communication with the refrigerant discharge outlet 114.
  • the compression mechanism 2 in this example is a rotary compression mechanism.
  • the compression mechanism 2 is disposed in the accommodation chamber 10.
  • a first silencing cavity 101 is formed between the compression mechanism 2 and the support 12.
  • the first silencing cavity 101 is in communication with an oil separation inlet 1132 of the oil separation chamber 113 through a first communication passage 115.
  • a first exhaust outlet 21 of the compression mechanism 2 is in communication with a first silencing cavity 101.
  • the compression mechanism 2 further has a second silencing cavity 22.
  • the second silencing cavity 22 is spaced apart from the first silencing cavity 101 in the axial direction of the compression mechanism 2.
  • the second silencing cavity 22 and the first silencing cavity 101 are in communication with each other through a second communication passage 23.
  • the compression mechanism 2 may further have a second exhaust outlet 283 in communication with the second silencing cavity 22.
  • the low-pressure refrigerant is converted into the high-pressure refrigerant in the compression mechanism 2.
  • the high-pressure refrigerant in the second silencing cavity 22 flows into the first silencing cavity 101 through the second communication passage 23, and then the high-pressure refrigerant in the first silencing cavity 101 enters the oil separation chamber 113 from the oil separation inlet 1132 through the first communication passage 115.
  • the separated gaseous refrigerant is finally discharged out of the housing assembly 1 through the refrigerant discharge outlet 114.
  • the flow noise and the pressure pulsations of the high-pressure refrigerant in the housing assembly 1 can be mitigated to mitigate the operation noise and the vibration of the electric compressor 100.
  • the embodiment illustrated in FIG. 4 and the above embodiments illustrated in FIG. 1 to FIG. 3 have the following differences.
  • the first communication hole 3 is formed at a connection between the first housing 11 and the support 12.
  • the first communication hole 3 is formed at the support 12.
  • the first communication passage 115 is in communication with the first silencing cavity 101 through the first communication hole 3, and the first communication hole 3 has a smaller flow area than a flow area of the first communication passage 115.
  • the embodiment illustrated in FIG. 5 and the above embodiment illustrated in FIG. 4 have the following difference.
  • the first communication hole 3 is formed at the first housing 11.
  • the first housing 11 includes no first communication passage 115.
  • the high-pressure cavity 102 is formed between the wall of the accommodation chamber 10 and the compression mechanism 2.
  • the first silencing cavity 101 and the oil separation inlet 1132 of the oil separation chamber 113 are in communication with each other through the high-pressure cavity 102.
  • the high-pressure refrigerant in the first silencing cavity 101 flows into the high-pressure cavity 102, and then flows into the oil separation chamber 113 through the oil separation inlet 1132.
  • the second silencing cavity 22 is also in communication with the high-pressure cavity 102 through the second communication hole 24.
  • the high-pressure refrigerant in the second silencing cavity 22 can further flow to the high-pressure cavity 102 through the second communication hole 24, which improves the exhaust efficiency while ensuring the noise reduction effect.
  • first and second are only used for descriptive purposes, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of indicated technical features. Therefore, the features associated with “first” and “second” may explicitly or implicitly include one or more of the features.
  • “plurality” means two or more, unless otherwise specifically defined.
  • the first feature "on” or “under” the second feature may mean that the first feature is in direct contact with the second feature, or the first and second features are in indirect contact through an intermediate.
  • the first feature "above” the second feature may mean that the first feature is directly above or obliquely above the second feature, or simply mean that the level of the first feature is higher than that of the second feature.
  • the first feature "below” the second feature may mean that the first feature is directly below or obliquely below the second feature, or simply mean that the level of the first feature is smaller than that of the second feature.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Compressor (AREA)
EP23825854.5A 2022-06-22 2023-03-15 Elektrischer verdichter, klimaanlage und fahrzeug Pending EP4520974A4 (de)

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CN202210715848.7A CN117307489B (zh) 2022-06-22 2022-06-22 电动压缩机、空调系统及车辆
CN202221588958.3U CN218325275U (zh) 2022-06-22 2022-06-22 电动压缩机、空调系统及车辆
PCT/CN2023/081744 WO2023246196A1 (zh) 2022-06-22 2023-03-15 电动压缩机、空调系统及车辆

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CN119103135B (zh) * 2024-09-29 2025-11-11 广东美芝制冷设备有限公司 泵组件和压缩机
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CN106762670B (zh) * 2017-01-24 2018-09-11 广东美芝制冷设备有限公司 压缩机、制冷系统和汽车
CN110259686A (zh) * 2018-03-12 2019-09-20 广东威灵汽车部件有限公司 压缩机和具有其的车辆
CN110259685A (zh) * 2018-03-12 2019-09-20 广东威灵汽车部件有限公司 油分离装置、压缩机及具有其的车辆
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