EP2053247A1 - Multistage compressor - Google Patents

Multistage compressor Download PDF

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Publication number
EP2053247A1
EP2053247A1 EP08722588A EP08722588A EP2053247A1 EP 2053247 A1 EP2053247 A1 EP 2053247A1 EP 08722588 A EP08722588 A EP 08722588A EP 08722588 A EP08722588 A EP 08722588A EP 2053247 A1 EP2053247 A1 EP 2053247A1
Authority
EP
European Patent Office
Prior art keywords
scroll
orbiting scroll
end plate
compression
wrap
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.)
Withdrawn
Application number
EP08722588A
Other languages
German (de)
English (en)
French (fr)
Inventor
Hajime Sato
Yoshiyuki Kimata
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.)
Mitsubishi Heavy Industries Ltd
Original Assignee
Mitsubishi Heavy Industries 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 Mitsubishi Heavy Industries Ltd filed Critical Mitsubishi Heavy Industries Ltd
Publication of EP2053247A1 publication Critical patent/EP2053247A1/en
Withdrawn legal-status Critical Current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
    • 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
    • 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
    • F04C23/001—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 of similar working principle
    • 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
    • F04C2210/00—Fluid
    • F04C2210/22—Fluid gaseous, i.e. compressible

Definitions

  • the present invention relates to a multistage compressor suitable for a vapor compression refrigerating cycle using carbon dioxide (CO 2 ) as a refrigerant gas (working gas).
  • CO 2 carbon dioxide
  • the critical temperature of CO 2 is about 31°C, being lower than the critical temperature of CFC, which is the conventional refrigerant. Therefore, when the open-air temperature is high as in summer, the temperature of CO 2 on the radiator side is higher than the critical temperature of CO 2 , so that CO 2 does not condense on the radiator outlet side. Also, the state on the radiator outlet side is determined by the discharge pressure of a compressor and the temperature of CO 2 on the radiator outlet side. Since the temperature of CO 2 on the radiator outlet side is determined by the radiation capacity of the radiator and the open-air temperature (uncontrollable), the temperature of radiator outlet cannot substantially be controlled. Therefore, the state on the radiator outlet side can be controlled by controlling the discharge pressure of the compressor (pressure on the radiator outlet side).
  • the pressure on the radiator outlet side must be increased to ensure sufficient cooling capacity (enthalpy difference).
  • the operating pressure of the compressor in the vapor compression refrigerating cycle using CO 2 , the operating pressure of the compressor must be increased to three to five times as compared with the conventional refrigerant cycle using CFC.
  • a scroll compressor As a compressor used in the vapor compression refrigerating cycle, a scroll compressor is known.
  • the scroll compressor includes, in a casing, a fixed scroll having a spiral wrap formed on one side of the end plate thereof, and an orbiting scroll provided, on one side of the end plate thereof, with a spiral wrap that is combined with the wrap of the fixed scroll to form a spiral compression chamber.
  • the scroll compressor compresses the introduced working gas in the compression chamber and then discharges the working gas with the orbiting of the orbiting scroll.
  • both the end plates of the fixed scroll and the orbiting scroll are smaller than the heights of both the spiral wraps, both the end plates of the fixed scroll and the orbiting scroll are liable to be deflectingly deformed by a load applied at the time of compression.
  • the sealing ability of the compression chamber decreases. Therefore, the discharge quantity is decreased by the leakage of working gas from the compression chamber, or the temperature of discharged gas is raised by recompression of leaking gas, so that the performance of the compressor degrades inevitably.
  • Patent Document 1 has proposed a technique in which the thicknesses T 1 and T 2 of the end plates of the fixed scroll and the orbiting scroll are made larger than 0.9 times the heights H 1 and H 2 of the spiral wraps of the fixed scroll and the orbiting scroll, respectively. According to the proposal of Patent Document 1, since the thicknesses of the end plates of the fixed scroll and the orbiting scroll are larger than 0.9 times the heights of the spiral wraps of the fixed scroll and the orbiting scroll, respectively, even in the scroll compressor using CO 2 as the working gas, the end plates of the fixed scroll and the orbiting scroll are less liable to be deformed by the load applied at the time of compression, so that the sealing ability of compression chamber is secured.
  • Patent Document 1 Japanese Patent Laid-Open No. 2000-352387
  • Patent Document 1 contributes to the practical use of the scroll compressor using CO 2 as the working gas.
  • the proposal of Patent Document 1 that is, the technique in which the thicknesses T 1 and T 2 of the end plates of the fixed scroll and the orbiting scroll are made larger than 0.9 times the heights H 1 and H 2 of the spiral wraps of the fixed scroll and the orbiting scroll, respectively, is based on the decrease in heights of spiral wraps. Therefore, the application of the proposal of Patent Document 1 is limited to a compressor having a relatively low capacity.
  • the present invention has been accomplished in view of the above circumstances, and accordingly an object thereof is to provide a compressor using a gas including a supercritical state, typically CO 2 , as a working gas and capable of having a high capacity.
  • a gas including a supercritical state typically CO 2
  • the present invention solves the above problems by making the working gas for the multistage compressor including at least one scroll compressor be a gas including a supercritical state, typically CO 2 . That is to say, the present invention is not configured so that the working gas is compressed from a low pressure to a high pressure by singly using a scroll compressor, but, for example, two compression mechanisms are provided to compress the working gas from a low pressure to a medium pressure by one compression mechanism and from the medium pressure to a high pressure by the other compression mechanism. Thereby, the differential pressure in one compression mechanism can be decreased.
  • the present invention provides a multistage compressor including an enclosed housing; a plurality of compression mechanisms provided in the enclosed housing; and a motor for driving the plurality of compression mechanisms, wherein at least one of the plurality of compression mechanisms is a scroll compression mechanism, and a gas including a supercritical state is used as a working gas, characterized in that the scroll compression mechanism includes a fixed scroll having a spiral wrap formed on one side of an end plate thereof, and an orbiting scroll provided, on one side of an end plate thereof, with a spiral wrap that is combined with the spiral wrap of the fixed scroll to form a compression chamber, and the introduced working gas is compressed in the compression chamber as the orbiting scroll orbits; and taking the thickness of the end plate of the orbiting scroll as Worb and the height of the spiral wrap of the orbiting scroll as L, a condition of L ⁇ Worb is satisfied.
  • a condition of Wfix ⁇ L ⁇ Worb is preferably satisfied. This condition contributes to the prevention of deformation of the end plate of the fixed scroll.
  • a condition of 2 ⁇ L/Tr ⁇ 7 is preferably satisfied. Thereby, the strength of the spiral wrap of the orbiting scroll is secured while securing the displacement.
  • the multistage compressor in accordance with the present invention taking the outside diameter of the end plate of the orbiting scroll as Dout, the outside diameter of the spiral wrap of the orbiting scroll as Dwrap, and the inside diameter of a support part on the back surface of the orbiting scroll as Db, conditions of Dwrap/Dout ⁇ 0.7 and Db ⁇ Dwrap are preferably satisfied.
  • Dwrap/Dout ⁇ 0.7 and Db ⁇ Dwrap are preferably satisfied.
  • the multistage compressor in which at least one of the plurality of compression mechanisms is a scroll compression mechanism, and CO 2 is used as the working gas, taking the thickness of the end plate of the orbiting scroll of the scroll compression mechanism as Worb and the height of the spiral wrap of the orbiting scroll thereof as L, the condition of L ⁇ Worb is satisfied.
  • the height of the spiral wrap of the orbiting scroll (fixed scroll) can be increased, so that the capacity of the compressor using CO 2 as the working gas can be increased.
  • 100 ... enclosed housing, 101 ... rolling piston compression mechanism, 102 ... scroll compression mechanism, 103 ... motor, 111 ... fixed scroll, 112 ... end plate, 113 ... wrap, 116 ... orbiting scroll, 117 ... end plate, 118 ... wrap, SA ... enclosed space
  • Figure 1 is a longitudinal sectional view showing a configuration of a multistage compressor of this embodiment.
  • a rolling piston compression mechanism 101 and a scroll compression mechanism 102 are disposed in an enclosed housing 100. Between the rolling piston compression mechanism 101 and the scroll compression mechanism 102, a motor 103 (electric motor) for driving the two compression mechanisms 101 and 102 is disposed.
  • the multistage compressor is explained in more detail below.
  • the scroll compression mechanism 102 In the upper part of the cylindrical enclosed housing 100 extending along the up and down direction, the scroll compression mechanism 102 is accommodated. Under the scroll compression mechanism 102, the motor 103 (electric motor) is accommodated. Also, between the scroll compression mechanism 102 and the motor 103, a rotating shaft 110 is disposed.
  • the motor 103 includes a stator 103a that is press fitted in and supported by the inner peripheral part of the enclosed housing 100 and a rotor 103b arranged on the inside of the stator 103a.
  • the rotor 103b is coaxially fixed on the rotating shaft 110, and the rotation of the rotor 103b is output from the rotating shaft 110.
  • the scroll compression mechanism 102 includes a fixed scroll 111 the whole of which is made of an iron-based material such as cast iron or carbon steel, and an orbiting scroll 116 made of an iron-based material, which meshes with the fixed scroll 111.
  • the fixed scroll 111 includes an end plate 112, a spiral wrap 113 formed on the inner surface of the end plate 112 facing to the orbiting scroll 116, and a peripheral wall 114 surrounding the wrap 113. Also, in the central part of the end plate 112, a discharge port 115 is provided.
  • the orbiting scroll 116 includes an end plate 117 and a spiral wrap 118 formed on the inner surface of the end plate 117 facing to the fixed scroll 111.
  • a cylindrical boss part 119 is projectingly provided in the central part of the back surface of the end plate 117 facing to the inner surface.
  • the fixed scroll 111 and the orbiting scroll 116 are assembled so that the wrap 113 and the wrap 118 are meshed with each other being shifted through 180 degrees (a predetermined angle).
  • a region the up and down direction of which is surrounded by the end plate 112 and the end plate 117 and which is further surrounded by the wrap 113 and the wrap 118 forms a plurality of crescent-shaped enclosed spaces SA for establishing a compression process.
  • the fixed scroll 111 and the orbiting scroll 116 are disposed on a casing-form frame 120 so that the fixed scroll 111 is on the upper side and the orbiting scroll 116 is on the lower side.
  • the back surface of the end plate 117 of the orbiting scroll 116 is slidably supported on a horizontal bearing surface 121 formed on the upper surface of the frame 120.
  • the upper end of the rotating shaft 110 extends toward the center of the end plate 117 of the orbiting scroll 116 while penetrating the frame 120.
  • the upper end part of the rotating shaft 110 is rotatably supported by a bearing 122 provided in the penetration part of the frame 120.
  • At the upper end of the rotating shaft 110 there is formed an eccentric pin 123 having the axis at a position off-center from the axis of the rotating shaft 110.
  • the eccentric pin 123 is slidably fitted in the boss part 119. Therefore, when the rotating shaft 110 rotates, the orbiting scroll 116 orbits around the axis of the fixed scroll 111.
  • a rotation inhibiting mechanism that inhibits the rotation of the orbiting scroll 116 though allowing the orbital motion thereof, for example, an Oldham's ring (not shown) is interposed.
  • an Oldham's ring (not shown) is interposed between the peripheral wall 114 of the fixed scroll 111 and the end plate 117 of the orbiting scroll 116 facing to the peripheral wall 114.
  • two large and small cylindrical flanges 124 and 125 are formed with the axis of the end plate 112 being the center.
  • a discharge cavity 127 is formed between the flanges 124 and 125 and the cover 126.
  • the discharge cavity 127 communicates with the discharge port 115 and a discharge pipe 129 connected to the upper wall of the enclosed housing 100, so that the discharged gas discharged into the discharge cavity 127 can be discharged to the outside of the enclosed housing 100.
  • the discharge port 115 is provided with a check valve 128 for preventing back flow.
  • the rolling piston compression mechanism 101 includes a main bearing body 131 and a subsidiary bearing body 132 that are provided on both sides of a cylinder 130 so as to hold the cylinder 130 therebetween, so that, by utilizing a circular space formed in the cylinder 130, a cylinder chamber 133 is formed in a part interposed between the main bearing body 131 and the subsidiary bearing body 132.
  • a rotor 134 and a blade for partitioning the cylinder chamber 133 into the suction side and the discharge side are disposed.
  • the rotor 134 is connected to one end part of the rotating shaft 110, which serves as the output shaft of the motor 103, via an eccentric cam part 135, so that the rotor 134 is eccentrically rotated in the cylinder chamber 133 by a driving force generated by the motor 103.
  • the rotor 134 is eccentrically rotated in the cylinder chamber 133 by receiving the rotational force from the rotating shaft 110 with the eccentric action of the eccentric cam part 135.
  • the working gas is sucked into the cylinder chamber 133 through a suction pipe 136 and a suction port (not shown) of the cylinder chamber 133.
  • the working gas compressed in the cylinder chamber 133 is discharged once into the enclosed housing 100 through a discharge port (not shown).
  • the gas is compressed from a low pressure to a medium pressure (low-stage compression).
  • the eccentric pin 123 is eccentrically rotated by receiving a rotational force from the rotating shaft 110.
  • the orbiting scroll 116 is orbited with respect to the fixed scroll 111.
  • the volumes of the crescent-shaped enclosed spaces SA formed between the wrap 113 and the wrap 118 are changed with the orbital motion. Therefore, the working gas in the enclosed housing 100 is sucked into the enclosed spaces SA through a passage 137 formed between the frame 120 and the inner peripheral surface of the enclosed housing 100, and is compressed with decreasing the volumes of the enclosed spaces SA.
  • the working gas that becomes in a predetermined compressed state is discharged to the outside of the enclosed housing 100 through the discharge port 115 provided in the central part of the fixed scroll 111, the check valve 128, the discharge cavity 127, and the discharge pipe 129.
  • the working gas is compressed from the medium pressure to a high pressure (high-stage compression).
  • the two-stage compressor of this embodiment features the scroll compression mechanism 102. This feature is explained below.
  • Figure 2 is a schematic view showing a cross section of the orbiting scroll 116.
  • the above-mentioned condition of L ⁇ Worb also means that the thickness of the end plate 117 of the orbiting scroll 116 can be decreased. Since the thickness of the end plate 117 can be decreased, the weight of the orbiting scroll 116 can be reduced, which contributes to an increase in efficiency of the scroll compression mechanism 102.
  • Figure 3 is a schematic view showing a state in which the fixed scroll 111 and the orbiting scroll 116 are combined.
  • the orbiting scroll 116 satisfies a condition of 2 ⁇ L/Tr ⁇ 7.
  • L/Tr is an index indicating the strength of the wrap 118. If L/Tr is less than 2, the displacement runs short. On the other hand, if L/Tr exceeds 7, the strength of the wrap 118 runs short. That is to say, by satisfying the condition of 2 ⁇ L/Tr ⁇ 7, the strength of the wrap 118 can be secured while securing the displacement.
  • the ratio of L/Tr is preferably in the range of 3 ⁇ L/Tr ⁇ 6, further preferably in the range of 3.5 ⁇ L/Tr ⁇ 5.5.
  • Figure 4 schematically shows a state in which the orbiting scroll 116 is supported on the frame 120.
  • the orbiting scroll 116 taking the outside diameter of the end plate 117 of the orbiting scroll 116 as Dout, the outside diameter of the wrap 118 of the orbiting scroll 116 as Dwrap, and the inside diameter of a support part on the back surface of the orbiting scroll 116 as Db, the orbiting scroll 116 satisfies conditions of Dwrap/Dout ⁇ 0.7 and Db ⁇ Dwrap, that is, a condition of Db ⁇ Dwrap ⁇ 0.7Dout.
  • the condition of Dwrap/Dout ⁇ 0.7 means that the area in which the wrap 118 is formed is decreased.
  • the application area of thrust load on the orbiting scroll 116 can be decreased.
  • the deformation of the end plate 117 of the orbiting scroll 116 can further be reduced.
  • the load can be supported by a larger area.
  • the thrust surface pressure can be reduced.
  • the decrease in area in which the wrap 118 is formed is especially effective in reducing the thrust surface pressure.
  • the support point of thrust load is shifted toward the central part of the orbiting scroll 116, by which the deformation of the end plate 117 can be reduced further.
  • the above is an explanation of one embodiment of the present invention.
  • the present invention is not limited to this embodiment, and can be applied widely to a multistage compressor provided with at least one scroll compression mechanism.
  • the present invention can also be applied to a compressor provided with two stages of scroll compression mechanisms or a compressor provided with a scroll compression mechanism on the low pressure side and a rolling piston compression mechanism on the high pressure side.
  • the present invention can be applied to any of a low-pressure housing, a high-pressure housing, and a medium-pressure housing.
  • the present invention can be applied to a scroll compression mechanism having an orbiting back pressure structure.
  • the orbiting back pressure structure is configured so that a back pressure chamber is provided on the back surface of orbiting scroll, and a gas having a pressure higher than the suction pressure (medium pressure or discharge pressure) is introduced into the back pressure chamber, by which the orbiting scroll is pressed against the fixed scroll side.
  • the thrust gas force can be reduced (canceled) in a wide range by properly controlling the pressure of gas introduced into the back pressure chamber. Therefore, the deformation of the end plate caused by the thrust gas force is reduced, so that the thickness of the end plate can be decreased.
  • the present invention that intends to relatively decrease the thickness of end plate is suitably applied to the scroll compression mechanism having the orbiting back pressure structure.
EP08722588A 2007-03-22 2008-03-21 Multistage compressor Withdrawn EP2053247A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2007073865A JP2008232041A (ja) 2007-03-22 2007-03-22 多段圧縮機
PCT/JP2008/055224 WO2008114860A1 (ja) 2007-03-22 2008-03-21 多段圧縮機

Publications (1)

Publication Number Publication Date
EP2053247A1 true EP2053247A1 (en) 2009-04-29

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP08722588A Withdrawn EP2053247A1 (en) 2007-03-22 2008-03-21 Multistage compressor

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EP (1) EP2053247A1 (ja)
JP (1) JP2008232041A (ja)
CN (1) CN101617123A (ja)
WO (1) WO2008114860A1 (ja)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113482923B (zh) * 2021-08-27 2022-09-09 广东美的环境科技有限公司 压缩组件、涡旋压缩机及空调器

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH07103167A (ja) * 1993-09-30 1995-04-18 Mitsubishi Heavy Ind Ltd 二段圧縮機
JP4043144B2 (ja) 1999-06-08 2008-02-06 三菱重工業株式会社 スクロール圧縮機
JP2004197640A (ja) * 2002-12-18 2004-07-15 Daikin Ind Ltd 容積型膨張機及び流体機械
JP4440564B2 (ja) * 2003-06-12 2010-03-24 パナソニック株式会社 スクロール圧縮機
JP2005083235A (ja) * 2003-09-08 2005-03-31 Matsushita Electric Ind Co Ltd スクロール圧縮機
JP2006144635A (ja) * 2004-11-18 2006-06-08 Denso Corp スクロール型圧縮機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2008114860A1 *

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Publication number Publication date
WO2008114860A1 (ja) 2008-09-25
JP2008232041A (ja) 2008-10-02
CN101617123A (zh) 2009-12-30

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