EP3018350A1 - Rotationsverdichter mit geringem gegendruck - Google Patents

Rotationsverdichter mit geringem gegendruck Download PDF

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Publication number
EP3018350A1
EP3018350A1 EP13888730.2A EP13888730A EP3018350A1 EP 3018350 A1 EP3018350 A1 EP 3018350A1 EP 13888730 A EP13888730 A EP 13888730A EP 3018350 A1 EP3018350 A1 EP 3018350A1
Authority
EP
European Patent Office
Prior art keywords
motor
channel
housing
rotary compressor
chamber
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.)
Granted
Application number
EP13888730.2A
Other languages
English (en)
French (fr)
Other versions
EP3018350B1 (de
EP3018350A4 (de
Inventor
Bin Gao
Zhenhua Chen
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 Meizhi Compressor Co Ltd
Original Assignee
Guangdong Meizhi Compressor 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
Application filed by Guangdong Meizhi Compressor Co Ltd filed Critical Guangdong Meizhi Compressor Co Ltd
Publication of EP3018350A1 publication Critical patent/EP3018350A1/de
Publication of EP3018350A4 publication Critical patent/EP3018350A4/de
Application granted granted Critical
Publication of EP3018350B1 publication Critical patent/EP3018350B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • 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
    • 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
    • F04C29/04—Heating; Cooling; Heat insulation
    • F04C29/045—Heating; Cooling; Heat insulation of the electric motor in hermetic pumps
    • 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
    • F04C2270/20—Flow

Definitions

  • the present disclosure relates to a compressor, and more particularly to a low backpressure rotary compressor.
  • a rotary compressor widely used in related art has a structure with high pressure in the housing, i.e. high backpressure structure, a gaseous refrigerant formed after a refrigerant returning to the compressor from a system passes through an air-liquid separator is directly inhaled into a cylinder to complete compression, the high-temperature and high-pressure refrigerant after being compressed is discharged into an interior space of the housing of the compressor, then discharged out of the compressor after cooling the motor, afterward enters the system for circulation.
  • high backpressure structure a gaseous refrigerant formed after a refrigerant returning to the compressor from a system passes through an air-liquid separator is directly inhaled into a cylinder to complete compression, the high-temperature and high-pressure refrigerant after being compressed is discharged into an interior space of the housing of the compressor, then discharged out of the compressor after cooling the motor, afterward enters the system for circulation.
  • a low backpressure rotary compressor with low pressure in the housing i.e. the interior space of the housing is communicated with the suction pressure.
  • a compressor with such a structure has a special advantage in some areas, especially in the future application of the rotary compressor, because the motor of the low backpressure compressor in a low-temperature and low-pressure suction environment will not result in an over high temperature or insufficient cooling of the motor caused by high exhaust temperature of the high pressure compressor.
  • the content of the refrigerant in the compressor will be significantly reduced and the refrigerant charge of the refrigeration system can be greatly reduced in the low pressure environment. Therefore, the low backpressure compressor will be widely used in these fields.
  • the motor of the low backpressure compressor dissipates heat mainly through low temperature and low pressure suction in the low pressure environment.
  • the intake of the compressor will decline, and the compression power consumption of unit mass air will increase, thereby resulting in a significant decrease in the performance of the low backpressure compressor compared to that of the high backpressure compressor.
  • the present disclosure seeks to solve at least one of the problems existing in the related art to at least some extent.
  • an object of the present disclosure is to provide a low backpressure rotary compressor.
  • the low backpressure rotary compressor Through a rational design of the low backpressure rotary compressor, it is possible to enable the motor to obtain a better cooling effect, and the air flow resistance within a channel is reduced, thereby improving the overall energy efficiency of the low backpressure rotary compressor.
  • the low backpressure rotary compressor With the low backpressure rotary compressor according to embodiments of the present disclosure, it is possible to realize a good balance between the circulation loss of the gas and the heat dissipation requirements of the motor by making the flow rate v of the gas in the channel in an appropriate range when the motor operates at different rotating speeds, for example, when F ⁇ 60 rev/s, 2 (m/s) ⁇ v ⁇ 25 (m/s), as another example, when F>60 rev/s, 8 (m/s) ⁇ v ⁇ 40 (m/s), thus ensuring that the motor works at a suitable temperature to avoid the occurrence of high temperature to damage the motor or affect the work efficiency of the motor. Meanwhile, the circulation loss of the gas is minimized, thereby improving the overall efficiency of the compressor.
  • the low backpressure rotary compressor according to embodiments of the present disclosure may further have the following additional technical features:
  • the motor is a constant speed motor.
  • the motor has a rated rotating speed of 50 rev/s or 60 rev/s.
  • the motor is a variable speed motor.
  • the motor has an adjustable exhaust volume V
  • the channel includes a first channel
  • the motor includes a stator and a rotor, in which at least a part of an outer circumferential surface of the stator is spaced apart from the inner circumferential surface of the housing to form the first channel.
  • the channel further includes a second channel
  • the motor includes a stator and a rotor, the stator defining at least one through hole penetrating the stator in an up-down direction to form the second channel.
  • the channel further includes a third channel
  • the motor includes a stator and a rotor, the rotor defining at least one through hole penetrating the rotor in an up-down direction to form the third channel.
  • the air suction port is formed in a main bearing or a cylinder.
  • first and second are used herein for purposes of description and are not intended to indicate or imply relative importance or significance or to imply the number of indicated technical features.Thus, the feature defined with “first” and “second” may include one or more of this feature. In the description of the present disclosure, "a plurality of” means two or more than two, unless specified otherwise.
  • a low backpressure rotary compressor 100 includes a housing, a motor 2 and a compression mechanism.
  • the housing defines a chamber therein, and includes an upper housing 11, a middle housing 12 and a lower housing 13 mentioned below, and an air suction pipe 14 is disposed on the housing.
  • a first end of the air suction pipe 14 is communicated with the chamber, specifically, the first end of the air suction pipe 14 is communicated with an upper chamber 15 mentioned below, a second end of the air suction pipe 14 is adapted to be communicated with a low pressure side heat exchanger of a refrigeration system having the compressor according to embodiments of the present disclosure.
  • the refrigeration medium flowing back from the low pressure side heat exchanger may enter the housing via the air suction pipe 14.
  • the motor 2 is disposed within the chamber and divides the chamber into an upper chamber 15 and a lower chamber 16, and the upper chamber 15 may be communicated with the lower chamber 16 via a channel.
  • a channel for example, including a first channel 231, a second channel 232 and a third channel 233, is formed between an outer circumferential surface of the motor 2 and an inner circumferential surface of the housing and/or within the motor 2, in other words, for example, the channel may be defined between the outer circumferential surface of the motor 2 and the inner circumferential surface of the housing.
  • the channel may be formed only inside the motor 2, for example, the channel may be formed in at least one of a stator 21 and a rotor 22.
  • a part of the channel is defined between the outer circumferential surface of the motor 2 and the inner circumferential surface of the housing, while another part of the channel is formed inside the motor 2.
  • a first end (such as an upper end) of each channel is communicated with the upper chamber 15 and a second end (such as a lower end) of each channel is communicated with the lower chamber 16.
  • the motor 2 may include the stator 21 and the rotor 22.
  • the stator 21 may have a roughly circular shape and may be adapted to be fixed on the housing, for example, the stator 21 may be welded onto an inner wall surface of the middle housing 12.
  • the rotor 22 is rotatably disposed within the stator 21 and adapted to be fixed with a crankshaft 35.
  • the compression mechanism is disposed below the motor 2 and defines an air suction port 36.
  • the compression mechanism may include a main bearing 31, a cylinder 32 and a supplementary bearing 33.
  • the main bearing 31 is disposed above the cylinder 32, for example, the main bearing 31 can be detachably fixed above the cylinder 32 via a plurality of bolts.
  • the supplementary bearing 33 is disposed below the cylinder 32, for example, the supplementary bearing 33 can be detachably fixed below the cylinder 32 via a plurality of bolts.
  • a compression chamber is defined between the main bearing 31, the cylinder 32 and the supplementary bearing 33, and used to compress the refrigeration medium, such as a gaseous refrigerant.
  • An upper part of the crankshaft 35 can be fixed with the rotor 22 of the motor 2, a lower end of the crankshaft 35 can extend downward though the main bearing 31, the cylinder 32 and the supplementary bearing 33.
  • a piston 34 is fitted over the crankshaft 35 and positioned within the compression chamber, and an outer circumferential surface of the piston 34 is circular or elliptic.
  • the air suction port 36 can be formed in the main bearing 31, and certainly can also be formed in the cylinder 32. Two ends of the air suction port 36 are communicated with the lower chamber 16 and the compression chamber, respectively.
  • the exhaust volume of the low backpressure rotary compressor described above refers to the volume of the gas discharged and converted to a suction state at an air inlet when the eccentric crankshaft rotates a cycle and the compressor works according to the circulation theory.
  • the flow area refers to an area of through holes which enable the upper and lower sides of the motor 2 to be communicated with each other and enable the gas to pass through the through holes smoothly after the assembly of the compressor is completed.
  • the through holes generally can include through holes or slots for connecting two sides of the motor, such as the first channel 231, the second channel 232 and the third channel 233 as described in Fig. 1 .
  • the total flow area S of the channels include a sum of flow areas of those channels (the first channel 231, the second channel 232 and the third channel 233).
  • those channels do not include holes or slots (such as slots used for installing windings, cast aluminum holes, rivet holes, and positioning holes of cores) which only have an assembly function.
  • the low backpressure rotary compressor 100 it is possible to realize a good balance between the circulation loss of the gas and the heat dissipation requirements of the motor 2 by making the flow rate v of the gas in the channel in an appropriate range when the motor 2 operates at different rotating speeds, for example, when F ⁇ 60 rev/s, 2 (m/s) ⁇ v ⁇ 25 (m/s), as another example, when F>60 rev/s, 8 (m/s) ⁇ v ⁇ 40 (m/s), thus ensuring that the motor 2 works at a suitable temperature to avoid the occurrence of high temperature to damage the motor 2 or affect the work efficiency of the motor 2. Meanwhile, the circulation loss of the gas is minimized, thereby improving the overall efficiency of the compressor.
  • the housing may include the upper housing 11, the middle housing 12 and the lower housing 13.
  • the middle housing 12 is connected between the upper housing 11 and the lower housing 13.
  • a lower end of the upper housing 11 can be fixed with an upper end of the middle housing 12 by e.g., welding
  • a lower end of the middle housing 12 can be fixed to an upper end of the lower housing 13 by e.g., welding.
  • the air suction pipe 14 is disposed on the upper housing 11, for example, the air suction pipe 14 can be fixed at a center of a top of the upper housing 11 by welding.
  • the motor 2 can be a constant speed motor, in other words, the output rotating speed of the motor 2 is constant, i.e. non-adjustable.
  • the rated rotating speed of the motor 2 can be 50 rev/s or 60 rev/s, that is, in some embodiments, the motor 2 only have a unique output rotating speed of 50 rev/s or 60 rev/s.
  • the motor 2 can be a variable speed motor, in other words, the output rotating speed of the motor 2 is adjustable.
  • the motor 2 may have several different preset rotating speeds. When the power of the compressor needs to be increased, the rotating speed of the motor 2 can be increased. When the power of the compressor needs to be decreased, the rotating speed of the motor 2 can be reduced. Of course, the rotating speed of the motor 2 can be continuously adjustable.
  • the exhaust volume V of the compressor is adjustable, in other words, the compressor is a variable exhaust volume compressor.
  • the variable exhaust volume compressor is known in the related art and known to those skilled in art, will not be elaborated here.
  • the compressor has a double-cylinder structure, i.e. the compressor has two compression chambers (i.e. the pump body of the compressor includes two cylinders).
  • the rotary compressor with the double-cylinder structure is well known to those skilled in art, which will not be elaborated here.
  • the channel includes the first channel 231, the second channel 232 and the third channel 233, and these three channels will be described below in detail, respectively.
  • the outer circumferential surface of the stator 21 can be a standard circumferential surface, a part (i.e. the first channel 231 mentioned above) of the outer circumferential surface of the stator 21 is removed, while the remaining part of the outer circumferential surface of the stator 21 which is not removed can closely adhere to the inner wall surface of the housing.
  • the second channel 232 can be formed in the stator 21.
  • the stator 21 is formed with at least one through hole (i.e. the second channel 232) penetrating the stator 21 in an up-down direction.
  • the third channel 233 can be configured as a through hole penetrating the rotor 22 in the up-down direction.
  • the rotor 22 is formed with at least one through hole (i.e. the third channel 233) penetrating the rotor 22 in the up-down direction.
  • the flow area of the first channel 231 is S1
  • the flow area of the second channel 232 is S2
  • the channel may include any one of the first channel 231, the second channel 232 and the third channel 233, so the corresponding total flow area S is any corresponding one of S1, S2 and S3.
  • the channel may include the first channel 231 and the second channel 232, or include the second channel 232 and the third channel 233, or include the first channel 231 and the third channel 233, i.e. the channel may include any two of the first channel 231, the second channel 232 and the third channel 233, so the corresponding total flow area S is S1 + S2, S1 + S3 or S2 + S3.
  • the first channels 231 there are a plurality of the first channels 231 which are evenly distributed in a circumferential direction.
  • the flow area S1 of the first channels 231 should be understood as the total flow area of the plurality of first channels 231.
  • the second channels 232 There are a plurality of the second channels 232 which are evenly distributed in a circumferential direction. For example, there are four second channels 232, and the angle between two adjacent second channels 232 can be 90°. Then, the flow area S2 of the second channels 232 should be understood as the total flow area of the plurality of second channels 232.
  • the third channels 233 there are a plurality of the third channels 233 which are evenly distributed in a circumferential direction. For example, there are three third channels 233, and the angle between two adjacent third channels 233 can be 120°. Then, the flow area S3 of the third channels 233 should be understood as the total flow area of the plurality of third channels 233.
  • the present disclosure is not limited to this.
  • the first channels 231, the second channels 232 and the third channels 233 also can be unevenly distributed in the circumferential direction.
  • the low backpressure rotary compressor 100 it is possible to enable the motor 2 to achieve a higher efficiency with a lower air flow resistance within the channel, thus achieving a better performance of the compressor.
  • the compressor according to embodiments of the present disclosure has a simple structure, a rational design and an excellent performance.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP13888730.2A 2013-07-04 2013-07-04 Rotationsverdichter mit geringem gegendruck Active EP3018350B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/CN2013/078815 WO2015000162A1 (zh) 2013-07-04 2013-07-04 低背压旋转式压缩机

Publications (3)

Publication Number Publication Date
EP3018350A1 true EP3018350A1 (de) 2016-05-11
EP3018350A4 EP3018350A4 (de) 2017-03-29
EP3018350B1 EP3018350B1 (de) 2020-06-24

Family

ID=52143033

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13888730.2A Active EP3018350B1 (de) 2013-07-04 2013-07-04 Rotationsverdichter mit geringem gegendruck

Country Status (3)

Country Link
EP (1) EP3018350B1 (de)
AU (1) AU2013393765B2 (de)
WO (1) WO2015000162A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3761483A4 (de) * 2018-03-29 2021-04-14 Guangdong Meizhi Compressor Co., Ltd. Motor, verdichter und kühlvorrichtung

Family Cites Families (9)

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Publication number Priority date Publication date Assignee Title
JPS475410U (de) * 1971-02-10 1972-09-18
JPS6186593U (de) * 1984-11-12 1986-06-06
JPS6186592U (de) * 1984-11-12 1986-06-06
JPS61129483A (ja) * 1984-11-28 1986-06-17 Matsushita Electric Ind Co Ltd 密閉形電動圧縮機
JPH04112990A (ja) * 1990-09-03 1992-04-14 Matsushita Electric Ind Co Ltd 密閉型ロータリー圧縮機
JP2535131Y2 (ja) * 1991-02-06 1997-05-07 シャープ株式会社 圧縮機
JPH075410A (ja) * 1992-12-02 1995-01-10 Casio Comput Co Ltd 液晶プロジェクタ
JPH06186593A (ja) * 1992-12-15 1994-07-08 Nikon Corp エレクトロクロミック眼鏡
CN100529406C (zh) * 2007-11-09 2009-08-19 广东美芝制冷设备有限公司 壳体低压的旋转式压缩机及其冷媒、回油的控制方式和应用

Non-Patent Citations (2)

* Cited by examiner, † Cited by third party
Title
No further relevant documents disclosed *
See also references of WO2015000162A1 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3761483A4 (de) * 2018-03-29 2021-04-14 Guangdong Meizhi Compressor Co., Ltd. Motor, verdichter und kühlvorrichtung

Also Published As

Publication number Publication date
EP3018350B1 (de) 2020-06-24
WO2015000162A1 (zh) 2015-01-08
AU2013393765B2 (en) 2016-09-29
EP3018350A4 (de) 2017-03-29
AU2013393765A1 (en) 2015-12-17

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