WO2021156938A1 - スクロール圧縮機 - Google Patents

スクロール圧縮機 Download PDF

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Publication number
WO2021156938A1
WO2021156938A1 PCT/JP2020/004132 JP2020004132W WO2021156938A1 WO 2021156938 A1 WO2021156938 A1 WO 2021156938A1 JP 2020004132 W JP2020004132 W JP 2020004132W WO 2021156938 A1 WO2021156938 A1 WO 2021156938A1
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WO
WIPO (PCT)
Prior art keywords
base plate
shell
main
scroll
opening
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.)
Ceased
Application number
PCT/JP2020/004132
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
政哉 岡本
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 Electric Corp
Original Assignee
Mitsubishi Electric Corp
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 Electric Corp filed Critical Mitsubishi Electric Corp
Priority to JP2021575129A priority Critical patent/JP7350101B2/ja
Priority to PCT/JP2020/004132 priority patent/WO2021156938A1/ja
Priority to CN202080095005.0A priority patent/CN115038871A/zh
Publication of WO2021156938A1 publication Critical patent/WO2021156938A1/ja
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • 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
    • 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

Definitions

  • the present disclosure relates to a scroll compressor including a fixed scroll and a swing scroll.
  • a fixed scroll fixed to an outer shell and a scroll compressor that compresses a refrigerant by a swinging scroll that swings with respect to the fixed scroll are known.
  • the shell that forms the outer shell of such a scroll compressor is a hollow and cylindrical main shell in which a fixed scroll is fixed to the inner wall surface, a substantially hemispherical upper shell that covers the opening at the top of the main shell, and the main shell. It consists of a substantially hemispherical lower shell that covers the lower opening.
  • Patent Document 1 discloses a scroll compressor in which the inner diameter of the lower part of the upper shell is larger than the outer diameter of the upper part of the main shell.
  • Patent Document 1 the outer peripheral portion of the fixed scroll is engaged with and attached to the surface of the upper end portion of the main shell. That is, Patent Document 1 does not need to add a member for attaching the fixed scroll or to form a step in which the outer peripheral portion of the fixed scroll is engaged with the shell. As described above, the scroll compressor of Patent Document 1 is intended to be easy to manufacture.
  • This disclosure is made to solve the above-mentioned problems, and provides a scroll compressor in which positioning when welding the upper shell and the main shell is accurately performed.
  • the scroll compressor according to the present disclosure includes a hollow shell, a fixed scroll having a plate-shaped first base plate and a spiral-shaped first spiral tooth extending from the first base plate in one direction.
  • a swing scroll having a plate-shaped second base plate located on one side of the first base plate, and a spiral second spiral tooth extending from the second base plate toward the first base plate.
  • the shell is tubular with a main opening, which is an opening communicating with the internal space, on the other end face, and an annular surface facing the other at the edge surrounding the main opening.
  • a main shell in which the first base plate is contacted and fixed to the edge surface, and an upper opening which is an opening are formed on one end surface, and the upper opening is formed as a concave lid covering the main opening.
  • the facing surface which is an annular surface facing the edge surface at the surrounding edge, has an upper shell that is fixed in contact with the edge surface on the outer peripheral side of the main shell with respect to the first base plate.
  • the edge surface of the main shell and the facing surface of the upper shell are in contact with each other. For this reason, the upper shell is restricted from moving from the position where it comes into contact with the main shell to one side. Therefore, in the scroll compressor of the present disclosure, positioning when welding the upper shell and the main shell can be performed accurately.
  • FIG. 1 It is a block diagram which shows the vertical cross section of the scroll compressor 1 which concerns on Embodiment 1.
  • FIG. It is an exploded perspective view which shows the main shell 20 and the main frame 8 which concerns on Embodiment 1.
  • FIG. It is a block diagram which shows the main shell 20 and the upper shell 21 which concerns on Embodiment 1.
  • FIG. It is a block diagram which shows the compression mechanism part 14 which concerns on Embodiment 1.
  • FIG. It It is a block diagram which shows the main shell 20 and the upper shell 221 which concerns on Embodiment 2.
  • FIG. It is an upper view which shows the fixed scroll 390 which concerns on Embodiment 3.
  • FIG. It is a block diagram which shows the vertical cross section of the fixed scroll 390 which concerns on Embodiment 3.
  • FIG. It is an upper view which shows the fixed scroll 390 which concerns on Embodiment 3.
  • FIG. It is a block diagram which shows the vertical cross section of the fixed scroll 390 which concerns on Embodiment 3.
  • FIG. It is an upper view which shows the fixed scroll 390 which concerns on Embodiment 3.
  • FIG. It is a block diagram which shows the vertical cross section of the fixed scroll 390 which concerns on Embodiment 3.
  • FIG. It is a block diagram which shows the main shell 20 and the upper shell 421 which concerns on Embodiment 4.
  • FIG. It is a block diagram which shows the scroll compressor 501 which concerns on Embodiment 5.
  • FIG. 1 is a configuration diagram showing a vertical cross section of the scroll compressor 1 according to the first embodiment.
  • the scroll compressor 1 includes a shell 5, a fixing base 6, a power feeding unit 7, a main frame 8, an oil return pipe 9, a subframe 10, an electric motor unit 11, a transmission unit 12, a compression mechanism unit 14, and a discharge. It has a part 15. Further, a suction pipe 2 and a discharge pipe 3 are connected to the scroll compressor 1.
  • the arrow U indicates an upward direction
  • the arrow L indicates a downward direction.
  • the scroll compressor 1 is a so-called vertical scroll compressor used in a state where the central axis of the crankshaft 70, which will be described later, is substantially perpendicular to the ground.
  • the suction pipe 2 is a pipe for sucking the refrigerant gas into the shell 5.
  • the discharge pipe 3 is a pipe for discharging the refrigerant gas from the shell 5.
  • the scroll compressor 1 does not have to be a vertical scroll compressor. In this case, a member in which the word "upper” or “lower” is used in the explanation of the position or orientation is simply read as “one” or “the other” is defined.
  • the refrigerant comprises, for example, a halogenated hydrocarbon having a carbon double bond, a halogenated hydrocarbon having no carbon double bond, a hydrocarbon, or a mixture containing them in the composition.
  • the halogenated hydrocarbon having a carbon double bond is an HFC refrigerant having a zero ozone depletion potential and a chlorofluorocarbon-based low GWP refrigerant.
  • the low GWP refrigerant include HFO refrigerants, and tetrafluoropropenes such as HFO1234yf, HFO1234ze, and HFO1243zf having a chemical formula represented by C3H2F4 are exemplified.
  • halogenated hydrocarbon having no carbon double bond examples include a refrigerant mixed with R32 (difluoromethane) represented by CH2F2, R41, or the like.
  • R32 difluoromethane
  • hydrocarbons examples include propane and propylene, which are natural refrigerants.
  • the mixture examples include a mixed refrigerant obtained by mixing R32, R41, or the like with HFO1234yf, HFO1234ze, HFO1243zf, or the like.
  • the shell 5 is a container that is hollow and the inside is filled with a refrigerant, and is made of a conductive member such as metal. The inside of the shell 5 is kept in a sealed state.
  • the shell 5 includes a main shell 20, an upper shell 21, a lower shell 22, and a connecting shell 23.
  • FIG. 2 is an exploded perspective view showing the main shell 20 and the main frame 8 according to the first embodiment.
  • the main shell 20 has a cylindrical shape extending in the vertical direction.
  • the main shell 20 is formed so that the inner diameter is widened at the upper part.
  • a main opening 32 which is an opening communicating with the internal space, is formed on the upper end surface and the lower end surface of the main shell 20.
  • the main opening 32 includes a main upper opening 33 formed on the upper end surface of the main shell 20 and a main lower opening 34 formed on the lower end surface of the main shell 20.
  • the main shell 20 has an edge surface 28, a positioning surface 29, an upper inner wall surface 30, and a lower inner wall surface 31.
  • the edge surface 28 is an annular plane that faces upward at the edge surrounding the main opening 32.
  • the positioning surface 29 is an annular flat surface facing upward at a portion where the diameter of the main shell 20 is expanded.
  • the upper inner wall surface 30 is a curved surface that connects the inner peripheral side of the edge surface 28 and the outer peripheral side of the positioning surface 29 and serves as the inner wall of the main shell 20.
  • the lower inner wall surface 31 is a curved surface that extends downward from the inner peripheral side of the positioning surface 29 and serves as an inner wall of the main shell 20.
  • FIG. 3 is a configuration diagram showing a main shell 20 and an upper shell 21 according to the first embodiment.
  • FIG. 3 is an enlarged view of the range shown by the dotted line in FIG.
  • the upper shell 21 has an upper opening 35 formed on the lower end surface thereof and has a concave lid shape.
  • the lower part of the upper shell 21 is connected to the main shell 20 by welding or the like, and covers the main upper opening 33.
  • the upper shell 21 has an facing surface 36.
  • the facing surface 36 is an annular surface facing downward at the edge surrounding the upper opening 35. That is, the facing surface 36 faces the edge surface 28.
  • the upper shell 21 is fixed to the main shell 20 at a position where the facing surface 36 contacts the outer peripheral side of the edge surface 28.
  • a discharge pipe 3 is connected to the upper part of the upper shell 21 by welding or the like.
  • the lower shell 22 has a concave lid shape, and the upper portion is connected to the lower part of the main shell 20 by welding or the like via a connecting shell 23 to cover the main lower opening 34.
  • An oil reservoir 37 for storing lubricating oil is formed at the bottom of the lower shell 22.
  • the connecting shell 23 has an annular shape and connects the lower shell 22 and the main shell 20.
  • the lubricating oil is, for example, a refrigerating machine oil containing an ester-based synthetic oil.
  • Lubricating oil is sucked up by the oil pump 61 described later, passes through the oil passage 79 described later in the crankshaft 70, reduces wear between parts that mechanically come into contact with each other in the compression mechanism portion 14 and the like, and the temperature of the sliding portion. Improves adjustment and sealing performance.
  • the lubricating oil is preferably an oil having excellent lubrication characteristics, electrical insulation, stability, refrigerant solubility, low temperature fluidity, and the like, and having an appropriate viscosity.
  • the fixing base 6 is connected to the shell 5 and fixes the shell 5 to another member such as a housing of an outdoor unit of an air conditioner.
  • a plurality of screw holes are formed in the fixing base 6.
  • the shell 5 is supported and fixed via the fixing base 6 by tightening a screw in the screw hole.
  • the power feeding unit 7 is a device that supplies power to the motor unit 11.
  • the power feeding unit 7 is connected to the outer peripheral surface of the main shell 20.
  • the power feeding unit 7 has a power feeding terminal 41, a cover 42, and an internal wiring 43.
  • the power supply terminal 41 is a terminal made of a metal member and to which an electric wire (not shown) for supplying electric power is connected.
  • One side of the power supply terminal 41 is located outside the shell 5 and is connected to an electric wire.
  • the other side portion of the power supply terminal 41 is located inside the shell 5, and the internal wiring 43 is connected to the shell 5.
  • the cover 42 is a member that covers one side of the power supply terminal 41 outside the shell 5 and prevents the power supply terminal 41 from becoming dirty.
  • the internal wiring 43 is wiring that extends from one end portion connected to the other side portion of the power feeding terminal 41 to the other end portion connected to the motor portion 11 inside the shell 5.
  • the internal wiring 43 transmits the electric power supplied from the electric wire to the motor unit 11.
  • the main frame 8 is a metal annular frame, which is provided inside and above the shell 5 and supports a transmission unit 12 and a swing scroll 91 of a compression mechanism unit 14 described later. As shown in FIG. 2, the main frame 8 includes a frame main body 45 and a bearing portion. The main frame 8 is fixed to the main shell 20 by the outer peripheral portion of the frame main body 45 being shrink-fitted onto the positioning surface 29 and the upper inner wall surface 30.
  • the frame body 45 has a hollow cylindrical shape. The inner diameter of the lower part of the frame body 45 is reduced in a stepped manner. That is, a step is formed on the inner wall surface of the frame body 45.
  • the frame main body 45 has a flat surface 47, a stepped surface 48, an upper inner wall surface 49 of the frame, an inner wall surface 50 below the frame, a frame edge portion 51, and an edge protrusion 52. Further, the frame main body 45 is formed with an oldham accommodating space 53, an eccentric accommodating space 54, a first oldam groove 55, and a suction port 56.
  • the flat surface 47 is an annular and flat surface formed on the upper part of the frame.
  • the step surface 48 is an annular flat surface facing upward at a position where a step is formed on the frame main body 45.
  • the inner wall surface 49 on the frame is a curved surface that connects to the outer peripheral side of the stepped surface 48 and the inner peripheral side of the flat surface 47 and serves as the inner wall of the frame main body 45.
  • the lower inner wall surface 50 of the frame is a curved surface of the frame main body 45 that extends downward from the inner peripheral side of the stepped surface 48 and becomes the inner wall of the frame main body 45.
  • the frame edge portion 51 is an upper edge of the frame main body 45, projects upward from the flat surface 47, and surrounds the flat surface 47.
  • the edge protrusion 52 is a pair of members protruding from the frame edge 51 toward the inner peripheral side of the frame body 45.
  • the oldham accommodating space 53 extends the stepped surface 48, the inner wall surface 49 on the frame, the surface when the inner wall surface 50 below the frame is extended upward, and the flat surface 47 in the radial direction. It is an annular space surrounded by a surface when it is used.
  • the ring portion 80 of the old dam ring 71 which will be described later, is accommodated in the old dam accommodating space 53.
  • the eccentric accommodating space 54 is a space inside the frame main body 45 excluding the oldham accommodating space 53.
  • the eccentric accommodating space 54 accommodates the eccentric shaft portion 76, the eccentric bearing portion 112, the bush 73, and the like of the crankshaft 70, which will be described later.
  • the first Oldham groove 55 is a groove formed so as to extend in the radial direction continuously to the flat surface 47, the stepped surface 48, the upper inner wall surface 49 of the frame, and the inner wall surface 50 below the frame.
  • the first Oldham groove 55 is composed of a pair of opposing grooves.
  • the first key portion 81 of the old dam ring 71, which will be described later, is slidably accommodated in the first old dam groove 55.
  • the suction port 56 is a space penetrating in the vertical direction in the frame main body 45.
  • the upper portion of the suction port 56 is formed at a position sandwiched between the edge protrusions 52.
  • the number of suction ports 56 may be formed instead of one.
  • the main bearing portion 46 is connected to the lower part of the frame main body 45.
  • a spindle hole 57 is formed in the central portion of the main bearing portion 46.
  • the spindle hole 57 is a space that penetrates the spindle hole 46 in the vertical direction and communicates with the accommodation space 211 at the upper portion. Further, the spindle hole 57 is smaller in the radial direction than the eccentric accommodating space 54.
  • the upper portion of the spindle portion 75 of the crankshaft 70 which will be described later, is inserted into the spindle hole 57.
  • an oil drain hole is formed at a position where the frame main body 45 and the main bearing portion 46 are connected.
  • the oil drain hole is a space formed through the inside and outside, and the lubricating oil accumulated in the old dam accommodating space 53 and the eccentric accommodating space 54 flows.
  • the oil return pipe 9 is inserted and fixed in the oil drain hole.
  • the oil return pipe 9 is a pipe that returns the lubricating oil accumulated in the oldham accommodating space 53 and the eccentric accommodating space 54 to the oil sump portion 37.
  • the subframe 10 is a metal annular frame that is provided inside and below the shell 5 to support the crankshaft 70.
  • the subframe 10 is fixedly supported on the inner peripheral surface of the main shell 20 by shrink fitting, welding, or the like.
  • the subframe 10 has an auxiliary bearing portion 60 and an oil pump 61.
  • the sub-bearing portion 60 is a ball bearing provided at the center and the upper portion of the sub-frame 10.
  • a sub-shaft hole 62 is formed in the central portion of the sub-bearing portion 60.
  • the sub-shaft hole 62 is a space that penetrates the sub-bearing portion 60 in the vertical direction.
  • the oil pump 61 is a pump provided at the center and below the subframe 10. The oil pump 61 is arranged so as to be immersed in the lubricating oil stored in the oil reservoir 37.
  • the electric motor unit 11 is stored in the central portion in the vertical direction of the shell 5, and the compression mechanism unit 14 is rotationally driven by being supplied with electric power from the outside via the internal wiring 43.
  • the electric motor unit 11 has a stator 65 and a rotor 66.
  • the stator 65 is an annular member that is fixedly supported on the inner wall surface of the shell 5 by shrink fitting or the like.
  • the stator 65 is formed, for example, by winding a winding (not shown) around an iron core (not shown) formed by laminating a plurality of electromagnetic steel sheets (not shown) via an insulating layer (not shown). Has been done.
  • the rotor 66 is a member provided so as to face the inner surface of the stator 65, and is a permanent magnet (not shown) inside an iron core (not shown) formed by laminating a plurality of electromagnetic steel sheets (not shown). ) Is built in.
  • the rotor 66 rotates when the stator 65 is energized.
  • the rotor 66 has a through hole 67 penetrating in the vertical direction at the center.
  • the transmission unit 12 is connected to the motor unit 11 and transmits the rotational force generated by the motor unit 11 to the compression mechanism unit 14 to drive the transmission unit 12.
  • the transmission unit 12 includes a crankshaft 70, an old dam ring 71, a thrust plate 72, and a bush 73.
  • crankshaft 70 The crankshaft 70 is a long metal rod-shaped member, which is provided inside the shell 5.
  • the crankshaft 70 has a spindle portion 75 and an eccentric shaft portion 76. Further, an oil passage 79 is formed in the crankshaft 70.
  • the main shaft portion 75 is a shaft forming the central portion and the lower portion of the crankshaft 70 in the vertical direction, and is arranged so that the central shaft thereof coincides with the central shaft of the main shell 20.
  • the spindle portion 75 is inserted into the through hole 67, and the rotor 66 is in contact with and fixed to the outer surface thereof. Further, the upper portion of the spindle portion 75 is inserted into the shaft hole of the spindle portion 46.
  • the lower part of the spindle portion 75 is inserted into the sub-shaft hole 62 of the sub-bearing portion 60.
  • the spindle portion 75 is provided with a first balancer 77 and a second balancer 78.
  • the first balancer 77 is provided on the upper part of the spindle portion 75, and balances the eccentric shaft portion 76 in response to the eccentric rotation.
  • the second balancer 78 is provided below the spindle portion 75 and balances the eccentric rotation of the eccentric shaft portion 76.
  • the eccentric shaft portion 76 is connected to the upper part of the spindle portion 75 so that the central shaft is eccentric with respect to the central shaft of the spindle portion 75.
  • the upper portion of the eccentric shaft portion 76 is located in the eccentric accommodating space 54 in a state of being fitted to the eccentric bearing portion 112.
  • the oil passage 79 is provided so as to penetrate the inside of the main shaft portion 75 and the eccentric shaft portion 76 in the vertical direction.
  • the old dam ring 71 causes the rocking scroll 91 to perform a rocking motion.
  • the oldam ring 71 has a ring portion 80, a first key portion 81, and a second key portion 82.
  • the ring portion 80 is an annular member.
  • the ring portion 80 is housed in the Oldam storage space 53 of the main frame 8.
  • the first key portion 81 is a rod-shaped member provided below the ring portion 80.
  • the first key portion 81 is composed of a pair of opposing members.
  • Each of the first key portions 81 is housed in each of the first Oldham grooves 55 of the main frame 8.
  • the second key portion 82 is a rod-shaped member provided on the upper portion of the ring portion 80.
  • the second key portion 82 is composed of a pair of opposing members. Each of the second key portions 82 is housed in each of a pair of second Oldham grooves 116 formed in the swing scroll 91, which will be described later.
  • the first key portion 81 slides on the first Oldham groove 55
  • the second key portion 82 slides on the second Oldam groove 116. Therefore, the old dam ring 71 prevents the swing scroll 91 from rotating.
  • the thrust plate 72 is an annular member arranged on a flat surface 47 and made of a steel plate-based material such as valve steel.
  • the thrust plate 72 functions as a thrust bearing.
  • the thrust plate 72 is formed with a notch 83 at a position facing the suction port 56.
  • the thrust plate 72 is arranged on the flat surface 47 so that the edge protrusion 52 is located inside the notch 83, and the movement in the circumferential direction is restricted.
  • the bush 73 is made of a metal such as iron, and is a member that connects the eccentric bearing portion 112 and the eccentric shaft portion 76.
  • the bush 73 has a slider 84 and a balance weight 85.
  • the slider 84 is a tubular member, and an eccentric shaft portion 76 is inserted therein. Further, the slider 84 is fitted in the eccentric bearing portion 112. That is, the eccentric shaft portion 76 is connected to the eccentric bearing portion 112 via the slider 84.
  • the slider 84 has a collar portion 86.
  • the collar portion 86 is a member formed in a collar shape at the lower part of the slider 84.
  • the balance weight is an annular member, and is fitted to the flange portion 86 by, for example, a method such as shrink fitting.
  • the balance weight has a weight portion 87 which is a member having a substantially C shape in a top view, and cancels the centrifugal force generated by the rotation of the crankshaft 70 and the swing scroll 91.
  • FIG. 4 is a configuration diagram showing a compression mechanism unit 14 according to the first embodiment.
  • the compression mechanism unit 14 is housed in the shell 5, compresses the refrigerant gas sucked from the suction pipe 2 through the suction port 56 into the refrigerant intake space 88, and discharges the compressed refrigerant gas.
  • the refrigerant intake space 88 is a space formed around the compression mechanism portion 14 inside the shell 5.
  • the compression mechanism unit 14 has a fixed scroll 90 and a swing scroll 91.
  • the fixed scroll 90 includes a first base plate 95 and a first spiral tooth 96.
  • the first base plate 95 is a disk-shaped and plate-shaped member. Further, as shown in FIG. 3, the lower portion of the outer peripheral portion of the first base plate 95 is reduced in diameter stepwise over the entire circumference.
  • a discharge port 104 is formed on the first base plate 95.
  • the first base plate 95 has a discharge inner peripheral surface 97, a discharge outer peripheral surface 98, a fixed compression surface 99, a fixed step surface 100, a discharge side surface 101, a fixed upper side surface 102, and a fixed lower side surface 103.
  • the discharge inner peripheral surface 97 is the inner peripheral side of the upper surface of the first base plate 95, and the discharge portion 15 is attached to the discharge inner peripheral surface 97.
  • the discharge outer peripheral surface 98 is the upper surface of the first base plate 95, and is located on the outer peripheral side and below the discharge inner peripheral surface 97.
  • the fixed compression surface 99 is a surface formed on the first base plate 95 on the opposite side of the discharge inner peripheral surface 97 and the discharge outer peripheral surface 98.
  • the fixed step surface 100 is an annular flat surface facing downward at a portion where the diameter of the first base plate 95 is reduced.
  • the discharge side surface 101 is a surface that connects the outer peripheral side of the discharge inner peripheral surface 97 and the inner peripheral side of the discharge outer peripheral surface 98.
  • the fixed upper side surface 102 is located on the outermost side in the radial direction of the first base plate 95, and is a surface that connects the outer peripheral side of the discharge outer peripheral surface 98 and the outer peripheral side of the fixed compression surface 99.
  • the fixed lower side surface 103 is a surface that connects the outer peripheral side of the fixed compression surface 99 and the inner peripheral side of the fixed step surface 100.
  • the fixed scroll 90 is positioned on the edge surface 28 of the main shell 20 so that the fixed step surface 100 comes into contact with the inner peripheral side of the facing surface 36, and the fixed lower side surface 103 is the upper inner wall surface 30 of the main shell 20. It is fixed to the main shell 20 by being shrink-fitted into.
  • the length of the fixed lower side surface 103 is appropriately adjusted according to the shrinkage fitting strength, and is, for example, the same length as the fixed upper side surface 102.
  • the length of the fixed lower side surface 103 may be 90% or more of the total length of the fixed upper side surface 102 and the fixed lower side surface 103.
  • the discharge port 104 is an opening formed at the central portion in the radial direction of the first base plate 95 so as to penetrate the first base plate 95 in the vertical direction and discharge the compressed refrigerant gas.
  • the first spiral tooth 96 is a spiral member extending downward from the fixed compression surface 99.
  • a first seal member 106 is provided on the first tip 105, which is the tip of the first spiral tooth 96.
  • the first seal member 106 suppresses the leakage of the refrigerant between the first tip portion 105 and the second base plate 110, which will be described later.
  • the swing scroll 91 includes a second base plate 110, a second spiral tooth 111, and an eccentric bearing portion 112.
  • the swing scroll 91 is made of, for example, a metal such as aluminum.
  • the second base plate 110 is a plate-shaped member.
  • the second base plate 110 has a sliding surface 113, a swinging compression surface 114, and a swinging side surface 115.
  • the oscillating compression surface 114 is a surface facing the fixed compression surface 99 of the fixed scroll 90.
  • the sliding surface 113 is a surface formed on the second base plate 110 on the opposite side of the oscillating compression surface 114. Further, the swing scroll 91 is supported by the main frame 8 with the sliding surface 113 arranged on the thrust plate 72.
  • the sliding surface 113 slides on the upper surface of the thrust plate 72 as the eccentric shaft portion 76 swings.
  • a second Oldham groove 116 is formed on the sliding surface 113.
  • the second Oldham groove 116 is composed of a pair of opposing grooves.
  • the second key portion 82 is slidably accommodated in the second Oldham groove 116.
  • the rocking side surface 115 is located on the outermost side in the radial direction and is a surface that connects the sliding surface 113 and the rocking compression surface 114.
  • the second spiral tooth 111 is a spiral member that extends from the second base plate 110 toward the first base plate 95 and forms a compression chamber 92 with the first spiral tooth 96.
  • a second seal member 118 is provided on the second tip portion 117, which is the tip end portion of the second spiral tooth 111. The second seal member 118 suppresses leakage of the refrigerant from between the second tip portion 117 and the first base plate 95.
  • a plurality of compression chambers 92 are formed in the internal space where the first spiral tooth 96 and the second spiral tooth 111 are in contact with each other.
  • the compression chamber 92 communicates with the discharge port 104 at the center of the fixed scroll 90.
  • the eccentric bearing portion 112 projects downward from the second base plate 110 and rotatably supports the eccentric shaft portion 76 and the bush 73.
  • the eccentric bearing portion 112 is a cylindrical member formed so as to project downward from substantially the center of the sliding surface 113 of the second base plate 110.
  • a journal bearing (not shown) is provided on the inner peripheral surface of the eccentric bearing portion 112. The journal bearing is provided so that the central axis is parallel to the central axis of the crankshaft 70, and rotatably supports the slider 84.
  • the swing scroll 91 tries to rotate with the above-mentioned swing radius with respect to the fixed scroll 90 which is fixed. Since the rotation of the swing scroll 91 is regulated by the old dam ring 71 as described above, the swing scroll 91 swings with the bush 73 at the swing radius described above with respect to the fixed scroll 90. At this time, the plurality of compression chambers 92 formed in the internal space where the first spiral tooth 96 and the second spiral tooth 111 come into contact with each other are formed with the first spiral tooth 96 and the first spiral tooth 96 as the swing scroll 91 swings. 2 The shape and volume change by changing the position where the spiral teeth 111 come into contact with each other. Therefore, in each compression chamber 92, the pressure fluctuates with the rotation of the eccentric shaft portion 76, and the refrigerant gas is compressed.
  • the discharge unit 15 is a member that covers the discharge port 104 and weakens the momentum of the refrigerant gas discharged from the compression mechanism unit 14.
  • the discharge unit 15 has a muffler 120 and a discharge valve 121.
  • the muffler 120 is provided on the discharge inner peripheral surface 97 and temporarily stores the refrigerant discharged from the compression mechanism unit 14.
  • a discharge hole 122 is formed in the muffler 120.
  • the discharge hole 122 discharges the refrigerant stored in the muffler 120.
  • the discharge valve 121 is a valve that opens and closes the discharge hole 122 to prevent the backflow of the refrigerant.
  • the operation of the scroll compressor 1 will be described with reference to FIG.
  • the low-pressure refrigerant gas that has flowed into the shell 5 from the suction pipe 2 reaches the refrigerant intake space 88 through the suction port 56, and is sucked into the compression chamber 92 of the compression mechanism unit 14.
  • the low-pressure refrigerant gas sucked into the compression chamber 92 is boosted from low pressure to high pressure due to a change in the volume of the compression chamber 92 as the swing scroll 91 swings.
  • the high-pressure refrigerant gas passes through the discharge port 104, opposes the discharge valve 121, and passes through the discharge hole 122.
  • the refrigerant that has passed through the discharge hole 122 is discharged from the discharge pipe 3 to the outside of the scroll compressor 1.
  • the edge surface 28 of the main shell 20 and the facing surface 36 of the upper shell 21 are in contact with each other. Therefore, the upper shell 21 is restricted from moving from the position where it comes into contact with the main shell 20 to one side. Therefore, the scroll compressor 1 of the first embodiment can accurately position the upper shell 21 and the main shell 20 when welding them.
  • the fixed scroll 90 is fixed to the main shell 20 by being aligned so that the fixed step surface 100 comes into contact with the edge surface 28.
  • the inner diameter above the step formed on the shell is larger than the outer diameter of the outer periphery of the fixed scroll. It is spread out.
  • the shell is formed to have a large overall wall thickness, thereby avoiding a decrease in the strength of the portion where the inner diameter is widened. Therefore, the shell tends to cause an increase in cost and weight due to an increase in material.
  • the fixed scroll 90 of the first embodiment is fixed to the main shell 20 by being aligned so that the fixed step surface 100 comes into contact with the edge surface 28. That is, the inner wall surface of the main shell 20 is not formed with a step with which the fixed scroll 90 is engaged. Therefore, it is not necessary to increase the overall wall thickness of the main shell 20. Therefore, the main shell 20 is unlikely to cause an increase in cost and weight due to an increase in materials.
  • FIG. 5 is a configuration diagram showing a main shell 20 and an upper shell 221 according to the second embodiment. As shown in FIG. 5, the second embodiment is different from the first embodiment in that a fitting space 223 is formed in the upper shell 221.
  • the same parts as those in the first embodiment are designated by the same reference numerals, the description thereof will be omitted, and the differences from the first embodiment will be mainly described.
  • a fitting space 223 is formed on the inner peripheral side of the lower portion of the upper shell 221.
  • the fitting space 223 is a space in which the first base plate 95 is fitted between the edge surface 28 and the lower end portion of the upper shell 221.
  • the first base plate 95 is fitted between the edge surface 28 and one end of the upper shell 221.
  • the shrink-fitting allowance between the fixed scroll and the main shell may be large so that the fixed scroll does not move from the predetermined position.
  • the first base plate 95 is fitted between the edge surface 28 and one end of the upper shell 221. Therefore, the fixed scroll 90 does not move from a predetermined position even when a gas load is applied. That is, the shrink fitting allowance of the fixed scroll 90 does not need to be unnecessarily increased. Therefore, the fixed scroll 90 can suppress deformation and breakage due to shrink fitting.
  • FIG. 6 is an upper view showing a fixed scroll 390 according to the third embodiment.
  • FIG. 7 is a configuration diagram showing a vertical cross section of the fixed scroll 390 according to the third embodiment.
  • the third embodiment is different from the first embodiment in that the base plate recess 302 is formed in the first base plate 95.
  • the same parts as those in the first embodiment are designated by the same reference numerals, the description thereof will be omitted, and the differences from the first embodiment will be mainly described.
  • the fixed scroll 390 comprises a first base plate 395 and a first spiral tooth 96.
  • the first base plate 395 is a disk-shaped and plate-shaped member, and the outer peripheral portion is formed thinner than the inner peripheral portion.
  • An annular and concave base plate recess 302 is formed on the outer peripheral surface 98 of the discharge.
  • the first spiral tooth 96 is a spiral member extending downward from the lower surface of the first base plate 395.
  • FIG. 8 is an upper view showing a fixed scroll 390 according to the third embodiment.
  • FIG. 9 is a configuration diagram showing a vertical cross section of the fixed scroll 390 according to the third embodiment.
  • a base plate recess 302 may be formed on the discharge inner peripheral surface 97.
  • FIG. 10 is an upper view showing a fixed scroll 390 according to the third embodiment.
  • FIG. 11 is a configuration diagram showing a vertical cross section of the fixed scroll 390 according to the third embodiment.
  • the base plate recess 302 does not have to be annular. Further, a plurality of base plate depressions 302 may be formed.
  • the first spiral tooth 96 extends from one surface of the first base plate 395, and the base plate recess 302 is formed on the other surface.
  • welding strain is likely to occur on the first base plate due to heat or stress generated when the main shell and the upper shell are welded.
  • a base plate recess 302 is formed on the other side surface of the first base plate 395. Therefore, the load corresponding to the expansion is absorbed by the base plate recess 302. That is, welding distortion is unlikely to occur in the fixed scroll 390. Therefore, the fixed scroll 390 can suppress deformation and breakage.
  • the base plate recess 302 is annular. Therefore, the expanded load is evenly absorbed by the base plate recess 302 over the entire circumference of the first base plate 395. That is, welding distortion is less likely to occur in the fixed scroll 390. Therefore, the fixed scroll 390 can further suppress deformation and breakage.
  • the base plate recess 302 is formed on the outer peripheral side of the first base plate 395.
  • the outer peripheral portion of the first base plate near the welded portion is particularly prone to expansion.
  • the base plate recess 302 is formed on the outer peripheral side of the first base plate 395. In this case, the load corresponding to the expansion is more absorbed by the base plate recess 302. That is, welding distortion is less likely to occur in the fixed scroll 390. Therefore, the fixed scroll 390 can further suppress deformation and breakage.
  • a plurality of base plate depressions 302 may be formed.
  • the load corresponding to the expansion is more absorbed by the base plate recess 302. That is, welding distortion is less likely to occur in the fixed scroll 390. Therefore, the fixed scroll 390 can further suppress deformation and breakage.
  • FIG. 12 is a configuration diagram showing a main shell 20 and an upper shell 421 according to the fourth embodiment. As shown in FIG. 12, the fourth embodiment differs from the first embodiment in that the outer peripheral side of the lower portion of the upper shell 421 extends along the main shell 20.
  • the same parts as those in the first embodiment are designated by the same reference numerals, the description thereof will be omitted, and the differences from the first embodiment will be mainly described.
  • the outer peripheral side of the lower part of the upper shell 421 extends along the main shell 20. That is, the welded portion between the lower portion of the upper shell 421 and the main shell 20 is not close to the edge surface 28.
  • the length of the outer peripheral side of the lower portion of the upper shell 421 is appropriately adjusted so as to be located between the edge surface 28 and the shrink fitting position of the main frame 8 in the vertical direction.
  • the outer peripheral side of one end of the upper shell 421 extends along the main shell 20.
  • the first base plate is prone to welding strain due to heat or stress generated when the main shell and the upper shell are welded.
  • the outer peripheral side of one end of the upper shell 421 extends along the main shell 20. That is, the portion where the first base plate 95, the main shell 20 and the upper shell 421 are welded is not close to each other. Therefore, it is difficult for heat or stress generated when the main shell 20 and the upper shell 421 are welded to the first base plate 95, and welding strain is unlikely to occur. Therefore, the fixed scroll 90 can suppress deformation and breakage.
  • FIG. 13 is a configuration diagram showing a scroll compressor 501 according to the fifth embodiment.
  • the scroll compressor 501 of the fifth embodiment is different from the first embodiment in that it does not have an upper shell and the fixed scroll 590 is provided with the discharge pipe 3.
  • the same parts as those in the first embodiment are designated by the same reference numerals, the description thereof will be omitted, and the differences from the first embodiment will be mainly described.
  • the shell 5 does not have an upper shell 21. Further, the first base plate 595 is welded to the main shell 20 so as to cover the opening formed in the upper part of the upper shell 21 and seal the refrigerant.
  • the fixed scroll 590 is provided with a discharge pipe 3 at the top.
  • the fixed scroll 590 is made of a weldable metal material such as SM material.
  • the fixed scroll 590 may be fixed to the main shell 20 by shrink fitting. In this case, the fixed scroll 590 may be made of cast iron.
  • the scroll compressor 501 does not have an upper shell, and the fixed scroll 590 is provided with the discharge pipe 3. Also in this case, the scroll compressor 501 can compress and discharge the sucked refrigerant. Therefore, the number of parts of the scroll compressor 501 is reduced. Therefore, the scroll compressor 501 has a reduced production cost.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Compressor (AREA)
PCT/JP2020/004132 2020-02-04 2020-02-04 スクロール圧縮機 Ceased WO2021156938A1 (ja)

Priority Applications (3)

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JP2021575129A JP7350101B2 (ja) 2020-02-04 2020-02-04 スクロール圧縮機
PCT/JP2020/004132 WO2021156938A1 (ja) 2020-02-04 2020-02-04 スクロール圧縮機
CN202080095005.0A CN115038871A (zh) 2020-02-04 2020-02-04 涡旋压缩机

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Cited By (1)

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Publication number Priority date Publication date Assignee Title
WO2024105950A1 (ja) * 2022-11-15 2024-05-23 三菱電機株式会社 スクロール圧縮機

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JPS63239391A (ja) * 1987-03-25 1988-10-05 Mitsubishi Electric Corp スクロ−ル圧縮機
JPH0315686A (ja) * 1989-06-13 1991-01-24 Sanyo Electric Co Ltd スクロール圧縮機
JPH03267590A (ja) * 1990-03-16 1991-11-28 Tokico Ltd スクロール流体機械の位置決め装置
JPH07310677A (ja) * 1994-05-17 1995-11-28 Daikin Ind Ltd スクロール圧縮機
US6123520A (en) * 1998-07-15 2000-09-26 Carrier Corporation Compressor upper shell weld ring
WO2018078787A1 (ja) * 2016-10-28 2018-05-03 三菱電機株式会社 スクロール圧縮機、冷凍サイクル装置およびシェル
WO2018179135A1 (ja) * 2017-03-29 2018-10-04 三菱電機株式会社 スクロール圧縮機、およびスクロール圧縮機の製造方法

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Publication number Priority date Publication date Assignee Title
JP2011047368A (ja) * 2009-08-28 2011-03-10 Sanyo Electric Co Ltd スクロール圧縮機

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS63239391A (ja) * 1987-03-25 1988-10-05 Mitsubishi Electric Corp スクロ−ル圧縮機
JPH0315686A (ja) * 1989-06-13 1991-01-24 Sanyo Electric Co Ltd スクロール圧縮機
JPH03267590A (ja) * 1990-03-16 1991-11-28 Tokico Ltd スクロール流体機械の位置決め装置
JPH07310677A (ja) * 1994-05-17 1995-11-28 Daikin Ind Ltd スクロール圧縮機
US6123520A (en) * 1998-07-15 2000-09-26 Carrier Corporation Compressor upper shell weld ring
WO2018078787A1 (ja) * 2016-10-28 2018-05-03 三菱電機株式会社 スクロール圧縮機、冷凍サイクル装置およびシェル
WO2018179135A1 (ja) * 2017-03-29 2018-10-04 三菱電機株式会社 スクロール圧縮機、およびスクロール圧縮機の製造方法

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2024105950A1 (ja) * 2022-11-15 2024-05-23 三菱電機株式会社 スクロール圧縮機
JPWO2024105950A1 (https=) * 2022-11-15 2024-05-23
GB2638576A (en) * 2022-11-15 2025-08-27 Mitsubishi Electric Corp Scroll compressor
JP7796897B2 (ja) 2022-11-15 2026-01-09 三菱電機株式会社 スクロール圧縮機

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