WO2019207759A1 - Compresseur à spirale - Google Patents

Compresseur à spirale Download PDF

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Publication number
WO2019207759A1
WO2019207759A1 PCT/JP2018/017172 JP2018017172W WO2019207759A1 WO 2019207759 A1 WO2019207759 A1 WO 2019207759A1 JP 2018017172 W JP2018017172 W JP 2018017172W WO 2019207759 A1 WO2019207759 A1 WO 2019207759A1
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WO
WIPO (PCT)
Prior art keywords
scroll
frame
thrust plate
fixed
fixed scroll
Prior art date
Application number
PCT/JP2018/017172
Other languages
English (en)
Japanese (ja)
Inventor
修也 福田
石園　文彦
友寿 松井
修平 小山
雷人 河村
伊藤　慎一
矢野　賢司
岩崎　俊明
Original Assignee
三菱電機株式会社
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 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2020515425A priority Critical patent/JP7076536B2/ja
Priority to PCT/JP2018/017172 priority patent/WO2019207759A1/fr
Priority to CN201880092583.1A priority patent/CN112005012B/zh
Publication of WO2019207759A1 publication Critical patent/WO2019207759A1/fr

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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

Definitions

  • This invention relates to a fixing structure of a thrust plate in a scroll compressor.
  • the swing scroll is supported by a frame which is a bearing part, and the fixed scroll is fixed to the frame with a bolt or the like so as to form a compression chamber together with the swing scroll.
  • the refrigerant is compressed in the compression chamber by swinging with respect to the scroll.
  • the frame is provided with a thrust plate for receiving the thrust load of the orbiting scroll generated during the orbiting motion. Since the thrust plate rotates with the swing operation of the swing scroll, in Patent Document 1, the protrusion of the thrust plate is fitted in the groove formed in the annular projecting portion of the frame.
  • Patent Document 1 it is necessary to project and form an annular projection on the frame in order to provide a groove that fits into the projection of the thrust plate. That is, since a structure for preventing the rotation of the thrust plate has to be newly provided, the structure of the frame and the like is complicated, and the cost increases.
  • the present invention has been made to solve the above-described problems, and an object of the present invention is to provide a scroll compressor capable of suppressing the rotation of the thrust plate with a simple configuration.
  • a scroll compressor includes a frame that swingably holds a swing scroll, a fixed scroll that forms a compression chamber that compresses refrigerant together with the swing scroll, and a space between the frame and the swing scroll. And a connecting member that connects the frame and the fixed scroll and inhibits rotation of the thrust plate.
  • the connecting member that connects the frame and the fixed scroll also serves as a function of suppressing the rotation of the thrust plate, thereby preventing the rotation of the thrust plate without newly providing a part for preventing the rotation of the thrust plate. can do.
  • FIG. 3 is a cross-sectional view of the scroll compressor taken along the line X-X ′ of FIG. 2 when viewed from the direction of the arrow.
  • 1 is an exploded perspective view of a partial configuration of a scroll compressor according to Embodiment 1 of the present invention. It is an enlarged view of the area
  • FIG. 1 is an external view of a scroll compressor according to Embodiment 1 of the present invention.
  • FIG. 2 is an external view of the scroll compressor of FIG. 1 when viewed from the side.
  • FIG. 3 is a cross-sectional view of the scroll compressor of FIG. 2 taken along the line XX ′.
  • FIG. 4 is an exploded perspective view of a partial configuration of the scroll compressor according to Embodiment 1 of the present invention. In FIG. 3, a part of the configuration such as the shell and the compression mechanism is shown in cross section, but the other configuration is shown as an external view.
  • the scroll compressor includes a shell 1, a main frame 2, a thrust plate 3, a compression mechanism unit 4, a drive mechanism unit 5, a sub frame 6, a crankshaft 7, a bush 8, a connecting member 9, It has.
  • the compressor according to the first embodiment is a so-called vertical scroll compressor that is used in a state where the central axis of the crankshaft 7 is substantially perpendicular to the ground.
  • the upper arrow side in the figure is referred to as one end side U as the upper side, and the lower arrow side is referred to as the other end side L as the lower side.
  • the shell 1 is a cylindrical casing made of a conductive member such as metal and closed at both ends, and includes a main shell 11, an upper shell 12, a lower shell 13, a suction pipe 14, a discharge pipe 15, and a power supply. A portion 16 and a fixing base 17 are provided.
  • the main shell 11 is a cylindrical tube.
  • the upper shell 12 is a substantially hemispherical lid, and a part of the upper shell 12 is connected to one end U of the main shell 11 by brazing or the like, and closes one opening of the main shell 11.
  • the lower shell 13 is a substantially hemispherical bottom body, a part of which is connected to the other end side L of the main shell 11 by welding or the like, and closes the other opening of the main shell 11.
  • the suction pipe 14 is a pipe for introducing a refrigerant into the inside of the shell 1, and a part of the suction pipe 14 is inserted into a hole provided in the side wall of the main shell 11 so as to communicate with the internal space of the shell 1. It is connected by brazing.
  • the discharge pipe 15 is a pipe for discharging the refrigerant to the outside of the shell 1 and is partially inserted into a hole provided in the upper part of the upper shell 12 so as to communicate with the internal space of the shell 1. It is connected by brazing.
  • the power supply unit 16 is a member that supplies power to the scroll compressor, and is provided on the outer wall of the main shell 11.
  • the power supply unit 16 includes a cover 161, a power supply terminal 162, and a wiring 163.
  • the cover 161 is a cover member.
  • the power supply terminal 162 is made of a metal member, and one is provided so as to be surrounded by the cover 161, and the other is provided inside the main shell 11.
  • One end of the wiring 163 is connected to the power supply terminal 162, and the other end is connected to the stator 51 of the drive mechanism unit 5 described later.
  • the fixed base 17 is a support base that supports the shell 1.
  • the fixing base 17 has a plurality of leg portions each formed with a screw hole, and the scroll compressor can be fixed to other members such as a casing of the air conditioner outdoor unit by fixing with screws.
  • the main frame 2 is a cylindrical metal frame, is provided inside the shell 1, and holds a swing scroll 42 of a compression mechanism section 4 described later so as to be swingable.
  • the main frame 2 includes a main body portion 21, a flat surface 22, a housing portion 23, a shaft hole 24, a suction port 25, an oil return hole 26, and an oil return pipe 27.
  • the main body 21 is a main part constituting the main frame 2.
  • the flat surface 22 is formed in an annular shape on one end side U of the main body portion 21 and is disposed around the housing portion 23.
  • the accommodating portion 23 is formed at the center in the radial direction of the main frame 2 along the longitudinal direction of the shell 1, that is, the axial direction of the crankshaft 7. As shown in FIG. 4, the accommodating portion 23 includes an Oldham accommodating portion 231, a bush accommodating portion 232, and a first Oldham groove 233.
  • the Oldham storage part 231 is provided on one end side U of the storage part 23.
  • the bush accommodating portion 232 is provided on the other end side L of the accommodating portion 23 and communicates with the Oldham accommodating portion 231.
  • the first Oldham groove 233 is a key groove formed in a part of the main body portion 21 and the flat surface 22, and is provided in a pair and communicates with the Oldham housing portion 231.
  • the shaft hole 24 is provided on the other end L of the housing portion 23 and communicates with the bush housing portion 232. That is, the accommodating portion 23 and the shaft hole 24 form a space that penetrates in the vertical direction of the main frame 2 and widens in a stepped manner toward the one end side U.
  • the portion of the main frame 2 in which the shaft hole 24 is formed functions as a main bearing portion that supports the crankshaft 7.
  • the suction port 25 is a hole for supplying a refrigerant to the compression mechanism unit 4 and is formed on the outer end side of the flat surface 22 of the main frame 2 so as to penetrate in the vertical direction.
  • the oil return hole 26 is formed in the other end L of the main frame 2 and communicates with the bush housing portion 232.
  • An oil return pipe 27 is inserted into the oil return hole 26 for returning the lubricating oil accumulated in the housing portion 23 to the oil sump inside the lower shell 13.
  • the suction port 25, the oil return hole 26, and the oil return pipe 27 are not limited to one, and a plurality of them may be provided.
  • the thrust plate 3 is a steel plate-type thin metal plate that functions as a thrust bearing, and is disposed on the flat surface 22 of the main frame 2 to support the thrust load of the compression mechanism section 4.
  • the thrust plate 3 includes a notch 31 and a hole 32.
  • the notch 31 is a part where a part of the outer periphery of the ring-shaped thrust plate 3 is notched, and is arranged corresponding to the suction port 25 of the main frame 2. At this time, the notch 31 is formed in the same shape as or larger than the suction port 25 so as not to cover the suction port 25.
  • the hole 32 will be described in detail later.
  • the compression mechanism unit 4 is a compression mechanism that compresses the refrigerant.
  • the compression mechanism unit 4 includes a fixed scroll 41, an orbiting scroll 42, an Oldham ring 43, a chamber 44, and a discharge valve 45, and a compression chamber 46 is formed by these scrolls.
  • the fixed scroll 41 is made of a metal such as cast iron, and includes a first base plate 411, a first spiral body 412, a tip seal 413, and a discharge port 414.
  • the first base plate 411 is a disk-shaped substrate.
  • the first spiral body 412 is a spiral tooth formed so as to protrude from the surface on the other end side L of the first base plate 411.
  • the tip seal 413 is made of, for example, hard plastic, and is provided in a groove formed at the tip of the first spiral body 412.
  • the discharge port 414 is a hole formed through substantially the center of the first base plate 411 in the vertical direction, which is the thickness direction thereof.
  • the orbiting scroll 42 is made of a metal such as aluminum, and includes a second base plate 421, a second spiral body 422, a tip seal 423, a cylindrical portion 424, and a second Oldham groove 425.
  • the second base plate 421 is a disk-shaped substrate.
  • the second spiral body 422 is a spiral tooth formed so as to protrude from the surface on one end side U of the second base plate 421.
  • the tip seal 423 is made of, for example, hard plastic, and is provided in a groove formed at the tip of the second spiral body 422.
  • the cylindrical portion 424 is a cylindrical boss formed to protrude from the approximate center of the surface on the other end side L of the second base plate 421.
  • the second Oldham groove 425 is an oval key groove formed on the surface on the other end side L of the second base plate 421.
  • the second Oldham grooves 425 are provided so as to face each other with the cylindrical portion 424 interposed therebetween.
  • the pair of second Oldham grooves 425 are arranged so that the line connecting them is orthogonal to the line connecting the pair of first Oldham grooves 233.
  • the Oldham ring 43 is a member for preventing the orbiting scroll 42 from rotating, and includes a ring portion 431, a first key portion 432, and a second key portion 433.
  • the ring portion 431 is annular and is provided in the Oldham accommodating portion 231 of the main frame 2.
  • the first key portion 432 is provided on the surface on the other end side L of the ring portion 431.
  • the first key portions 432 are configured as a pair, and are accommodated in the pair of first Oldham grooves 233 of the main frame 2, respectively.
  • the second key portion 433 is provided on the surface on the one end side U of the ring portion 431.
  • the second key portion 433 is configured as a pair, and is accommodated in the pair of second Oldham grooves 425 of the swing scroll 42.
  • the position of the second spiral body 422 of the orbiting scroll 42 in the rotational direction is determined. That is, the Oldham ring 43 positions the orbiting scroll 42 with respect to the main frame 2 and determines the phase of the second spiral body 422 with respect to the main frame 2.
  • the chamber 44 includes a discharge hole 441 provided on the surface of the fixed scroll 41 on one end side U and spatially communicating with the discharge port 414.
  • the discharge valve 45 is a valve that opens and closes the discharge hole 441 according to the pressure of the refrigerant, and is screwed to the chamber 44.
  • the discharge valve 45 opens the discharge hole 441 when the refrigerant in the compression chamber 46 communicating with the discharge port 414 reaches a predetermined pressure.
  • the compression chamber 46 meshes the first spiral body 412 of the fixed scroll 41 and the second spiral body 422 of the orbiting scroll 42 with each other, and the tip of the first spiral body 412, the tip seal 413 and the second base plate. 421 and the tip of the second spiral body 422, the tip seal 423, and the first base plate 411 are used for sealing.
  • the compression chamber 46 is composed of a plurality of compression chambers whose volume is reduced from the outside toward the inside in the radial direction of the scroll.
  • a halogenated hydrocarbon having a carbon double bond for example, a halogenated hydrocarbon having a carbon double bond, a halogenated hydrocarbon having no carbon double bond, a natural refrigerant, or a mixture containing them can be used in the composition.
  • Halogenated hydrocarbons having no carbon double bond are R32 (CH2F2), R41 (CH3F), R125 (C2HF3), R134a (CH2FCF2), R143a (CF3CH3), R410A (R32 / R125), R407C (R32 / And HFC refrigerants such as R125 / R134a).
  • the refrigerant coolant with which R32 (difluoromethane) represented by CH2F2, R41, etc. were mixed is illustrated.
  • the natural refrigerant include ammonia (NH3), carbon dioxide (CO2), propane (C3H8), propylene (C3H6), butane (C4H10), isobutane (CH (CH3) 3), and the like.
  • the refrigerant is preferably a low GWP refrigerant having an ozone depletion coefficient of zero.
  • the drive mechanism section 5 is provided on the other end side L from the main frame 2.
  • the drive mechanism unit 5 includes a stator 51 and a rotor 52.
  • the stator 51 is a stator formed by winding a winding around an iron core formed by laminating a plurality of electromagnetic steel plates with an insulating layer interposed therebetween, and is formed in a ring shape.
  • the stator 51 is fixed to the inner wall of the main shell 11 by shrink fitting or the like.
  • the rotor 52 is a cylindrical rotor having a built-in permanent magnet inside an iron core formed by laminating a plurality of electromagnetic steel plates and having a through-hole penetrating in the vertical direction in the center, and is disposed in the internal space of the stator 51. ing.
  • the sub-frame 6 is a metal frame, is provided on the other end L of the drive mechanism unit 5, and is fixed to the inner peripheral surface of the main shell 11 by shrink fitting, welding, or the like.
  • the sub frame 6 includes a sub bearing portion 61 and an oil pump 62.
  • the sub bearing 61 is a ball bearing provided on the upper center side of the sub frame 6.
  • the oil pump 62 is a pump for sucking up the lubricating oil stored in the oil reservoir of the shell 1, and is provided on the lower center side of the subframe 6.
  • Lubricating oil is stored in the lower part of the shell 1, that is, the lower shell 13, and is sucked up by the oil pump 62 and passes through an oil passage 73 in the crankshaft 7 to be described later and mechanically contacts the compression mechanism 4 and the like. Reduces wear between parts to be used, adjusts the temperature of sliding parts, and improves sealing performance.
  • As the lubricating oil an oil having an appropriate viscosity as well as excellent lubrication characteristics, electrical insulation, stability, refrigerant solubility, low-temperature fluidity and the like is suitable.
  • naphthenic, polyol ester (POE), polyvinyl ether (PVE), and polyalkylene glycol (PAG) oils can be used.
  • the crankshaft 7 is a metal rod-like member and is provided inside the shell 1.
  • the crankshaft 7 includes a main shaft portion 71, an eccentric shaft portion 72, and an oil passage 73.
  • the main shaft portion 71 is a shaft that constitutes a main portion of the crankshaft 7, and is arranged so that the central axis thereof coincides with the central axis of the main shell 11.
  • the main shaft portion 71 is fixed to the through hole at the center of the rotor 52 by shrink fitting or the like.
  • the eccentric shaft portion 72 is provided on one end side U of the main shaft portion 71 such that the central axis is eccentric with respect to the central axis of the main shaft portion 71.
  • the oil passage 73 is provided in the main shaft portion 71 and the eccentric shaft portion 72 so as to penetrate vertically along the axial direction.
  • the crankshaft 7 is inserted into the shaft hole 24 of the main frame 2, and the other end L is inserted and fixed in the through hole of the sub bearing portion 61 of the subframe 6.
  • the eccentric shaft portion 72 is arranged in the cylinder of the cylindrical portion 424, and the rotor 52 is arranged corresponding to the stator 51, and its outer peripheral surface keeps a predetermined gap from the inner peripheral surface of the stator 51. Arranged.
  • the bush 8 is made of a metal such as iron and is a connecting member that connects the orbiting scroll 42 and the crankshaft 7.
  • the bush 8 includes a slider 81 and a balance weight 82.
  • the slider 81 is a cylindrical member in which a flange is formed, and is inserted into the cylindrical portion 424 while being inserted into the eccentric shaft portion 72.
  • the balance weight 82 is a donut-shaped member having a weight portion 721 whose shape viewed from one end U is substantially C-shaped, and is offset from the center of rotation in order to offset the centrifugal force of the orbiting scroll 42. It is provided with a lead.
  • the balance weight 82 is fitted to the flange of the slider 81 by a method such as shrink fitting.
  • connection member 9 is a member that connects the main frame 2 and the fixed scroll 41.
  • the connection member 9 is, for example, a cylindrical metal rod.
  • FIG. 5 is an enlarged view of a region Y indicated by a one-dot chain line in FIG.
  • the fixed scroll 41 is fixed to the first inner wall surface 111 of the main shell 11 which is the inner wall of the shell 1. More specifically, the main shell 11 projects from the first inner wall surface 111, the first projecting portion 112 that projects from the first inner wall surface 111 and positions the fixed scroll 41, and toward the one end U in the first projecting portion 112.
  • the fixed scroll 41 is fixed to the first inner wall surface 111 by shrink fitting, welding, or the like while being positioned on the first positioning surface 113. ing. That is, the main shell 11 includes a stepped portion whose inner diameter increases toward the other end L, and the fixed scroll 41 is positioned and fixed using the step.
  • the main frame 2 is also fixed to the second inner wall surface 114 by shrink fitting or the like while being positioned by the second positioning surface 116 of the second protruding portion 115 protruding from the second inner wall surface 114 of the main shell 11. Yes.
  • a structure without a frame outer wall of the scroll compressor can be realized.
  • a main frame is generally provided with an outer wall for screwing with a fixed scroll.
  • the orbiting scroll is disposed in a space inside the outer wall, and thus the size of the orbiting scroll is restricted by the outer wall of the main frame. If there is a restriction on the size of the orbiting scroll, the size of the scroll spiral teeth is also restricted, so that the maximum horsepower of the compressor cannot be increased.
  • the main frame 2 does not include an outer wall for screwing with the fixed scroll 41, the side surface of the second base plate 421 of the orbiting scroll 42 and the inner wall surface of the main shell 11 are used. A space will be formed between the two.
  • the outer diameter of the second base plate 421 and the winding diameter of the second spiral body 422 can be made larger than before. it can. That is, the shell 1 is kept in the conventional design, and the maximum horsepower of the compressor is increased by increasing the diameters of the first spiral body 412 and the second spiral body 422, or the thrust is increased by increasing the second base plate 421.
  • a design that reduces the load becomes possible.
  • by reducing the diameter of the main shell 11 while keeping the size of the orbiting scroll 42 it is possible to design the compressor to be smaller without reducing the maximum horsepower.
  • FIG. 6 is an enlarged view of a two-dot chain line region Z in FIG.
  • FIG. 7 is a top view of the orbiting scroll disposed on the thrust plate.
  • FIG. 8 is a diagram when the swing scroll swings toward the suction port in FIG.
  • FIG. 9 is a top view of the orbiting scroll according to the first embodiment.
  • the fixed scroll 41 is connected to the main frame 2 by the connecting member 9. More specifically, one end U of the connection member 9 is accommodated in a first accommodating portion 415 formed near the outer end of the first base plate 411 of the fixed scroll 41, and the other end L is connected to the main frame 2.
  • the fixed scroll 41 and the main frame 2 are connected by being accommodated in the second accommodating portion 211 formed near the outer end of the main body portion 21.
  • the second spiral body 422 of the orbiting scroll 42 is phased with respect to the main frame 2 by the Oldham ring 43, and the first spiral body 412 of the fixed scroll 41 is phased with respect to the main frame 2 by the connecting member 9. Therefore, the meshing of the spiral teeth of the fixed scroll 41 and the swing scroll 42 is naturally positioned in a predetermined state. That is, by connecting the fixed scroll 41 and the main frame 2 with the connecting member 9, the phase alignment between the fixed scroll 41 and the orbiting scroll 42 is performed indirectly. In the phase determination, the fixed scroll 41 and the orbiting scroll 42 are matched with a predetermined design relationship at the time of manufacture.
  • the first housing portion 415 is a concave portion having a shape recessed from the surface side of the first base plate 411 in which the first spiral body 412 is formed toward the upper shell 12, and the second housing portion 211 is a flat surface 22.
  • a gap is formed in the first housing portion 415 and / or the second housing portion 211.
  • a gap is formed in the first housing portion 415 due to the weight of the connection member 9. That is, the distance between the bottom of the first housing part 415 and the bottom of the second housing part 211 is set to be greater than the length of the connection member 9. The gap prevents the connecting member 9 from being stretched between the main frame 2 and the fixed scroll 41 before the positioning of the main frame 2 and the fixed scroll 41 is completed.
  • the connecting member 9 is inserted into the hole 32 of the thrust plate 3.
  • the thrust plate 3 When the rocking scroll 42 is swung, the thrust plate 3 tries to rotate along with the rocking motion, but the connecting member 9 is inserted into the hole 32 so that the inner wall surface of the hole 32 and the connecting member are inserted. 9, the rotation of the thrust plate 3 is suppressed.
  • a gap D is formed between the thrust plate 3 and the main shell 11. Since the outer diameter of the thrust plate 3 is set to be slightly smaller than the inner diameter of the main shell 11, the gap D is very small. That is, since the gap D is very small compared to the outer diameter of the thrust plate 3 and the inner diameter of the main shell 11, there is substantially no room for the thrust plate 3 to move inside the main shell 11. That is, the fixing of the thrust plate 3 and prevention of rotation are realized by the connecting member 9 and the gap D.
  • the swing scroll 42 includes a first cutout 426.
  • the first notch 426 is for avoiding contact between the orbiting scroll 42 and the connecting member 9 when provided corresponding to the connecting member 9.
  • FIG. 7 shows a state in which the orbiting scroll 42 is swung toward the connecting member 9, but it does not come into contact with the connecting member 9 even in this state. That is, the first notch 426 does not come into contact with the connection member 9 at any timing when the swing scroll 42 is swinging. Therefore, when the connection member 9 is arranged for connecting the fixed scroll 41 and the main frame 2, at least a part of the connection member 9 is provided in a space formed between the main shell 11 and the orbiting scroll 42. 9 is easily positioned in the swing range of the swing scroll 42, but this is avoided by the first notch 426.
  • the orbiting scroll 42 includes a second notch 427.
  • the second notch 427 is provided so that the suction port 25 is not covered by the swing scroll 42 when provided corresponding to the suction port 25.
  • FIG. 8 shows a state in which the orbiting scroll 42 is swung toward the suction port 25, but even in this state, the orbiting scroll 42 is not positioned on the suction port 25. That is, it does not overlap with the suction port 25 at any timing when the swing of the swing scroll 42 is swinging.
  • the orbiting scroll 42 is enlarged, the suction port 25 is easily covered, and a pressure loss may occur when the refrigerant is sucked.
  • the second notch 427 avoids this.
  • the swing scroll 42 has a suitable portion.
  • the first straight line B from the spiral end 4221 in the rotational direction from the spiral end 4221, which is the outermost end of the second spiral 422, to the spiral center along the teeth of the second spiral 422.
  • the AB plane extending from the center O of the orbiting scroll 42 to the straight line A is connected to the first quadrant, and then the straight line A (the center O of the orbiting scroll 42 and the spiral end 4221 are connected.
  • the first notch when the AB plane up to the straight line is the second quadrant, the AB plane up to the straight line B is the third quadrant, and the AB plane up to the straight line A is the fourth quadrant It is desirable to form 426 in the second quadrant or the fourth quadrant. This is because the outer end portion of the second base plate 421 in the second quadrant and the fourth quadrant is a portion that is not used as a compression portion, and there is no functional problem even if the portion is cut out.
  • the second notch 427 is desirably formed in the second quadrant or the fourth quadrant where the first notch 426 is not formed.
  • the sizes of the second base plate 421 and the second spiral body 422 are maximized.
  • the contact with the connecting member 9 by the swing scroll 42 and the overlap with the suction port 25 can be avoided.
  • FIG. 10 is a diagram for explaining a method of manufacturing the main shell.
  • FIG. 10 shows a cross section of one wall of the main shell 11 in an easy-to-understand manner, and differs from actual dimensions and thicknesses.
  • a cutting brush or the like (not shown) is inserted from one end side U of the unprocessed main shell 11 as shown in (a), and the inner wall surface is cut in the thickness direction, as shown in (b).
  • a step is formed by the two inner wall surfaces 114 and the second protrusions 115.
  • a cutting brush or the like on the second inner wall surface 114 that is a predetermined distance away from the second protrusion 115 in the direction of the one end U, ( As shown in c), a step is formed by the first inner wall surface 111 and the first protrusion 112.
  • the inner diameter r1 of the first inner wall surface 111 is larger than the inner diameter r2 of the second inner wall surface 114.
  • the 1st protrusion part 112 is formed in the direction of the one end side U rather than the 2nd protrusion part 115, The inner wall surface becomes the structure which served as the 2nd inner wall surface 114.
  • FIG. The second protrusion 115 may be formed after the first protrusion 112 is formed.
  • the thickness of the main shell 11 is, for example, 4 to 6 mm, while the height of the protruding portion, that is, the depth of cutting by cutting shown by a dotted line is, for example, about 0.3 mm.
  • the main frame 2 is inserted from one end side U of the main shell 11 formed as described above.
  • the main frame 2 is in surface contact with the second positioning surface 116 of the second protrusion 115 and is positioned in the height direction.
  • the main frame 2 is fixed to the second inner wall surface 114 by shrink fitting, arc spot welding, or the like.
  • the bush 8 is attached to the eccentric shaft portion 72, and the Oldham ring 43, the swinging scroll 42, and the like are further arranged.
  • the orbiting scroll 42 is arranged on the Oldham ring 43, the phase of the orbiting scroll 42 with respect to the main frame 2 is determined.
  • the connection member 9 is inserted into the second housing portion 211 through the hole 32 of the thrust plate 3.
  • the fixed scroll 41 is inserted while inserting the connecting member 9 into the first housing portion 415, and then the fixed scroll 41 is fixed to the first inner wall surface 111 by shrink fitting.
  • the fixed scroll 41 is positioned in the height direction by making contact with the first positioning surface 113 of the first protrusion 112 on the surface.
  • the phase of the fixed scroll 41 with respect to the main frame 2 is determined by being connected to the main frame 2 by the connection member 9. Since the orbiting scroll 42 with respect to the main frame 2 is already in phase as described above, the phase alignment between the fixed scroll 41 and the orbiting scroll 42 is completed by connecting the main frame 2 and the fixed scroll 41.
  • the connecting member 9 can set the assembly phase of the fixed scroll 41 and the orbiting scroll 42 to a predetermined one without going through a special phase matching process.
  • the first protrusion 112 only needs to be positioned at least for the manufacture of the fixed scroll 41. Therefore, after the fixed scroll 41 is fixed to the first inner wall surface 111, the fixed scroll 41 comes into contact with the first positioning surface 113. It is not essential to be. The same applies to the relationship between the main frame 2 and the second protrusion 115.
  • the main shell 11 and the upper shell 12 are fixed by welding, arc spot welding, or the like.
  • the fixed scroll 41 is inserted into the upper shell 12 so as to be pressed against the first positioning surface 113, and the fixed scroll 41 is fixed to the main shell 11 while maintaining the state.
  • the variation in the height of the intake space may be suppressed to increase the positional accuracy, and the fixed scroll 41 may be prevented from shifting in the vertical direction when the scroll compressor is driven.
  • the scroll compressor according to the present embodiment fixes the fixed scroll 41 to the main shell 11 without forming the outer wall for connecting the fixed scroll 41 to the main frame 2 as in the prior art. Therefore, the scroll base plate and the spiral teeth can be enlarged. That is, conventionally, there was a spiral volume limit that the scroll mechanism had to be designed inside the outer wall of the main frame, but in the structure without the frame outer wall, the storage space of the orbiting scroll 42 becomes the inner space of the main shell 11. As a result, the design freedom of the scroll is expanded, and the size of the swing scroll 42 can be expanded to the inner wall of the main shell 11.
  • the phase in the rotational direction of the first spiral body 412 and the second spiral body 422 can be matched, and the spiral teeth are engaged with each other. It can be in a predetermined state.
  • the spiral design is a compression chamber design, and the meshing of the spiral teeth provided on the fixed scroll 41 and the orbiting scroll 42 is required to be highly accurate.
  • the main frame and the fixed scroll are generally fixed with bolts or the like. When the main frame and the fixed scroll are bolted, the phases of the fixed scroll and the main frame are determined at the same time.
  • the fixed scroll and the oscillating scroll can be meshed with each other by fixing them with bolts. That is, conventionally, the accuracy of meshing between the orbiting scroll and the fixed scroll has been increased by fixing the bolt.
  • the main frame 2 and the fixed scroll 41 cannot be fixed with a bolt or the like, so a new phase matching means is required.
  • the connecting member 9 is equivalent to the new phase adjusting means, and by connecting the main frame 2 and the fixed scroll 41, the spiral teeth of the fixed scroll 41 and the orbiting scroll 42 are indirectly connected to each other. Phase alignment can be performed.
  • the connecting member 9 since the connecting member 9 is used for the phase alignment of the fixed scroll 41 and the swing scroll 42, it also serves as a structure for preventing the thrust plate 3 from rotating. That is, since the connecting member 9 has not only a function of connecting the main frame 2 and the fixed scroll 41 but also a function of preventing the rotation of the thrust plate 3, the number of parts can be reduced as compared with the case where each is provided. Complexity and cost increase can be avoided.
  • the main frame 2 that swingably holds the swing scroll 42, the fixed scroll 41 that forms a compression chamber 46 that compresses the refrigerant together with the swing scroll 42, the main frame 2, and the swing scroll 42.
  • a connecting member 9 that connects the main frame 2 and the fixed scroll 41 and restricts the rotation of the thrust plate 3.
  • the shell 1 includes a main shell 11 having both ends opened. The main shell 11 protrudes from the first inner wall surface 111, the first inner wall surface 111, and the first protrusion 112 that positions the fixed scroll 41. A first positioning surface 113 formed on one protruding portion 112, and the fixed scroll 41 is fixed to the first inner wall surface 111 while being positioned on the first positioning surface 113.
  • the rotation of the thrust plate 3 can be suppressed by using the connecting member 9 that performs phase alignment of the fixed scroll 41 and the swing scroll 42, and the thrust plate 3 is prevented from rotating. It is possible to avoid an increase in the number of members by newly providing these parts.
  • the orbiting scroll 42 includes a second base plate 421 on which a second spiral body 422 is formed.
  • the second base plate 421 is a first notch that avoids contact with the connection member 9 when the orbiting scroll 42 swings.
  • a portion 426 is provided. Therefore, the size of the orbiting scroll 42 can be increased while avoiding contact between the orbiting scroll 42 and the connecting member 9.
  • a straight line connecting the center C of the orbiting scroll 42 and the spiral end 4221 which is the outermost end of the second spiral body 422 is a straight line A
  • a straight line passing through the center C of the orbiting scroll 42 and perpendicular to the straight line A is a straight line.
  • the size of the orbiting scroll 42 is reduced while avoiding contact between the orbiting scroll 42 and the connecting member 9. It can be as large as possible.
  • the main frame 2 includes a suction port 25 that supplies a refrigerant to the compression chamber 46, the thrust plate 3 includes a notch 31 at a position corresponding to the suction port 25, and the second base plate 421 corresponds to the notch 31.
  • a second cutout portion 427 is provided at a position to perform. Therefore, the suction port 25 can be prevented from being blocked by the orbiting scroll 42 and the thrust plate 3, and the occurrence of pressure loss can be suppressed.
  • the first cutout 426 and the second cutout 427 are provided symmetrically with respect to the center C of the orbiting scroll 42. Therefore, the size of the orbiting scroll 42 can be increased as much as possible while avoiding the contact between the orbiting scroll 42 and the connecting member 9 and the generation of pressure loss due to the suction port 25 being blocked.
  • the fixed scroll 41 includes a first storage portion 415 that stores one end side of the connection member 9, and the main frame 2 includes a second storage portion 211 that stores the other end side of the connection member 9. Therefore, the fixed scroll 41 and the main frame 2 can be stably connected.
  • the first storage portion 415 and the second storage portion 211 are concave portions, and a gap is formed in at least one of the first storage portion 415 or the second storage portion 211 in a state where the connection member 9 is stored. Therefore, it is possible to prevent the connecting member 9 from being stretched when making the tooth tip gaps of the spiral teeth of the fixed scroll 41 and the swing scroll 42 suitable.
  • FIG. FIG. 11 is a cross-sectional view of a scroll compressor according to Embodiment 2 of the present invention
  • FIG. 12 is a top view of an orbiting scroll disposed on a thrust plate.
  • parts having the same configurations as those of the scroll compressor of FIGS. 1 to 10 are denoted by the same reference numerals and description thereof is omitted.
  • the shapes of the fixed scroll 41A and the connecting member 9A are changed.
  • the first substrate 411A of the fixed scroll 41A includes a protrusion 416A that protrudes in the direction of the main frame 2, and one end side U of the connection member 9A is formed at the tip of the protrusion 416A. It is accommodated in the first accommodating portion 415A.
  • the connecting member 9A can be shortened, and the phase shift between the fixed scroll 41A and the main frame 2 can be reduced. This is because as the length of the connecting member 9A becomes shorter, the blur width in which the connecting member 9A moves becomes smaller.
  • the distance between the protrusion 416A of the fixed scroll 41A and the thrust plate 3 is larger than the thickness of the second base plate 421 of the orbiting scroll 42.
  • the rocking scroll 42 can be prevented from interfering with the protruding portion 416A during the rocking, and the size of the rocking scroll 42 can be increased.
  • a part of the second base plate 421 of the orbiting scroll 42 is constantly or at least once between revolutions between the protrusion 416A and the thrust plate 3 during the oscillation. It is possible to enter the space, that is, to exceed the straight line S drawn directly from the inner wall surface of the protrusion 416A.
  • the swinging scroll 42 is swung by making the second base plate 421 enter the space between the protruding portion 416A and the thrust plate 3 at the swinging timing when the swinging scroll 42 is closest to the connecting member 9A.
  • the size of the scroll 42 can be increased as much as possible.
  • the fixed scroll 41A includes a protrusion 416A that protrudes in the direction of the main frame 2, and the first accommodating part 415A is formed in the protrusion 416A. Therefore, the same effect as in the first embodiment is obtained, and the connecting member 9A is shortened, so that the phase shift between the fixed scroll 41A and the main frame 2 can be reduced.
  • the size of the second base plate 421 of the swing scroll 42 is increased. can do.
  • FIG. FIG. 13 is a cross-sectional view of a scroll compressor according to Embodiment 3 of the present invention
  • FIG. 14 is a top view of an orbiting scroll disposed on a thrust plate.
  • the shapes of the fixed scroll 41B, the swinging scroll 42B, and the connecting member 9B are changed.
  • an extension 428B is formed on the second base plate 421B of the swing scroll 42B.
  • the extending portion 428B extends outward from the end of the second base plate 421B on the thrust plate 3 side.
  • the fixed scroll 41 includes a protruding portion 416B that protrudes in the direction of the main frame 2 and accommodates one end side of the connection member 9B, and is provided between the protruding portion 416B and the thrust plate 3. The distance is smaller than the thickness of the second base plate 421B of the orbiting scroll 42B and larger than the thickness of the extending portion 428B.
  • the inner wall surface of the protruding portion 416B is always or at least once per revolution while a part of the extending portion 428B of the swing scroll 42 is swinging. It is possible to exceed the straight line S drawn directly from.
  • the swinging scroll 42 moves into the space between the protruding portion 416B and the thrust plate 3 especially at the swinging timing when the swinging scroll 42 is closest to the connecting member 9B.
  • 42B can be enlarged, in particular, the contact area between the second base plate 421 and the thrust plate 3 can be increased, and the thrust load can be reduced.
  • the orbiting scroll 42B includes a second base plate 421B on which the second spiral body 422 is formed, and an extending portion 428B extending outward from the end portion on the thrust plate 3 side of the second base plate 421B.
  • the distance between the protruding portion 416B of the fixed scroll 41 and the thrust plate 3 is smaller than the thickness of the second base plate 421B of the orbiting scroll 42B and larger than the thickness of the extending portion 428B. Therefore, the same effect as in the first embodiment is obtained, and the connecting member 9A is shortened, so that the phase shift between the fixed scroll 41A and the main frame 2 can be reduced.
  • the vertical scroll compressor has been described, but the present invention can also be applied to a horizontal scroll compressor.
  • the drive mechanism unit 5 is not limited to the low-pressure shell type scroll compressor in which the pressure in the main shell 11 in which the drive mechanism unit 5 is disposed is lower than the pressure in the discharge space in the upper shell 12.
  • the present invention can also be applied to a high-pressure shell type scroll compressor in which the pressure in the space in the main shell 11 is equal to or higher than the pressure in the discharge space in the upper shell 12.
  • the thrust plate 3 since the thrust plate 3 has a low pressure in the drive mechanism unit 5, the rocking scroll 42 is pressed against the drive mechanism unit 5 by the pressure of the high-pressure refrigerant compressed in the compression chamber 46, and the thrust load increases.
  • the low-pressure shell is more effective because it is particularly employed in the low-pressure shell.
  • the main frame 2 is not limited to a structure without a frame outer wall.
  • the shape of the suction port 25 of the main frame 2 can be variously changed.
  • the suction port 25C may be a half-moon shaped refrigerant suction hole.
  • suction ports 251D and 252D may be formed in addition to the suction port 25, suction ports 251D and 252D may be formed.
  • the suction ports 251D and 252D are preferably formed in the main frame 2 on both sides of the second housing portion 211. That is, by forming the suction ports 251D and 252D so as to sandwich the connection member 9, the suction ports 251D and 252D can be formed in the main frame 2 without forming a new notch in the swing scroll 42. it can.
  • a pair of suction ports 253E and 254E may be formed at positions that do not face the connecting member 9 as long as the swinging scroll 42E is not blocked during swinging.
  • the sectional area of the suction port 25 is desirably larger than the sectional area of the suction pipe 14 so that the refrigerant taken in from the suction pipe 14 reduces the pressure loss of the suction port 25.
  • the cross-sectional area of the suction port 25 can be adjusted to be larger than the cross-sectional area of the suction pipe 14, and the occurrence of refrigerant pressure loss at the suction port 25 can be suppressed. Can do.
  • the notch 31 of the thrust plate 3 does not cover the suction port 25 by matching the shape of the suction port 25 as in the first embodiment.
  • a notch 31C that is linearly cut is formed in the thrust plate 3C.
  • notches 311D are formed at both ends of the hole 32D of the thrust plate 3D.
  • 312D is formed, and notches 313E and 314E are formed in the thrust plate 3E in the suction ports 253E and 254E of FIG.
  • the 1st accommodating part 415 of the fixed scroll 41 is not restricted to a recessed part.
  • the first accommodating portion 415F may be a through hole that penetrates the first base plate 411F.
  • the phases of the fixed scroll 41F and the orbiting scroll 42 can be matched, and the rotation of the thrust plate 3 can be prevented.
  • the connecting member 9 can be inserted from the first accommodating portion 415F and phased. Manufacturing can be facilitated.
  • a slight gap is formed between them.
  • the high pressure space on one end side U of the fixed scroll 41F and the low pressure space on the other end side L are spatially communicated with each other by the gap. Therefore, after the connection member 9 is arranged, the first housing portion 415F is sealed. It is desirable that at least one of the holes is sealed by the member 417F to substantially form a recess, and the space above and below the fixed scroll 41F is blocked.
  • the second base plate 421 of the orbiting scroll 42 does not necessarily need to include the first cutout portion 426 and the second cutout portion 427.
  • the second base plate 421E may have a disk shape. Even when notches are not formed in the orbiting scroll, the size of the second base plate 421E and the second spiral body 422E of the orbiting scroll 42E is smaller than that of the conventional arrangement of the orbiting scroll on the main frame having the outer wall. Can be bigger. Further, the second base plate 421 may be elliptical. In that case, by making the part close to the connection member 9 short, the same effect as when the first notch 426 and the second notch 427 are formed in the orbiting scroll 42 as in the first embodiment. Can be obtained.
  • the connecting member 9 is not limited to a cylindrical shape.
  • a connecting member 9C having a polygonal shape, specifically, a quadrangular prism shape may be used.
  • an elliptical columnar connection member 9D may be used.
  • a connection member 9 ⁇ / b> G having a tapered surface 91 ⁇ / b> G at the end portion of the fixed scroll 41 that is accommodated in the first accommodating portion 415 may be used. Since the taper surface 91G serves as a guide when the first accommodating portion 415 of the fixed scroll 41 is inserted into the connecting member 9G, manufacturing can be facilitated.
  • connection member 9G has a dimension that can be accommodated in the first housing part 415, that is, a dimension that the taper surface 91G is not positioned outside the first housing part 415.
  • a plurality of connecting members 9 may be provided. By configuring the connecting member 9 in a plurality, not only the thrust plate 3 rotates but also can be fixed. However, when there are a plurality of connection members 9, high processing accuracy is required for the first storage portion 415 of the fixed scroll 41 that stores the connection members 9 and the second storage portion 211 of the main frame 2. Further, the difficulty of the process of connecting the fixed scroll 41 and the main frame 2 by the connecting member 9 also increases. Therefore, it is optimal to configure the connection member 9 as a single member as in the first embodiment.
  • the hole 32 of the thrust plate 3 matches the shape of the connecting member 9. That is, in the connecting member 9C of FIG. 15, the hole 32C is rectangular, and in the connecting member 9D of FIG. 16, the hole 32D is elliptical. Moreover, it is good also as a notch shape like the hole 32C of FIG. 15, and the hole 32E of FIG. That is, the hole 32 of the thrust plate 3 can be inserted through the connection member 9, and when the thrust plate 3 tries to rotate along with the swing motion of the swing scroll 42, the inner surface contacts the outer surface of the connection member 9. By doing so, it is sufficient if it can suppress rotation.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)

Abstract

L'invention concerne un compresseur à spirale étant pourvu : d'un cadre qui maintient une volute à spirale de telle sorte que la volute à spirale peut tourner ; d'une volute fixe qui, conjointement avec la volute à spirale, forme une chambre de compression qui comprime un fluide frigorigène ; d'une plaque de poussée qui est disposée entre le cadre et la volute à spirale ; et d'un élément de liaison qui relie le cadre et la volute fixe et qui empêche la rotation de la plaque de poussée.
PCT/JP2018/017172 2018-04-27 2018-04-27 Compresseur à spirale WO2019207759A1 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
JP2020515425A JP7076536B2 (ja) 2018-04-27 2018-04-27 スクロール圧縮機
PCT/JP2018/017172 WO2019207759A1 (fr) 2018-04-27 2018-04-27 Compresseur à spirale
CN201880092583.1A CN112005012B (zh) 2018-04-27 2018-04-27 涡旋式压缩机

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2018/017172 WO2019207759A1 (fr) 2018-04-27 2018-04-27 Compresseur à spirale

Publications (1)

Publication Number Publication Date
WO2019207759A1 true WO2019207759A1 (fr) 2019-10-31

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PCT/JP2018/017172 WO2019207759A1 (fr) 2018-04-27 2018-04-27 Compresseur à spirale

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JP (1) JP7076536B2 (fr)
CN (1) CN112005012B (fr)
WO (1) WO2019207759A1 (fr)

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JPWO2022050142A1 (fr) * 2020-09-02 2022-03-10
WO2022102564A1 (fr) * 2020-11-10 2022-05-19 三菱電機株式会社 Compresseur à spirale et procédé d'assemblage de compresseur à spirale

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JPH09126161A (ja) * 1995-11-08 1997-05-13 Hitachi Ltd スクロール圧縮機
WO2016056172A1 (fr) * 2014-10-07 2016-04-14 パナソニックＩｐマネジメント株式会社 Compresseur à spirales
JP2017115762A (ja) * 2015-12-25 2017-06-29 サンデンホールディングス株式会社 スクロール型圧縮機

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EP0479412B1 (fr) * 1990-10-01 1994-08-24 Copeland Corporation Accouplement Oldham pour compresseur à spirales
JP3260518B2 (ja) * 1993-11-04 2002-02-25 松下電器産業株式会社 スクロール圧縮機及びその組立方法
JP5612411B2 (ja) * 2010-09-21 2014-10-22 株式会社ヴァレオジャパン スクロール型圧縮機
JP5697968B2 (ja) * 2010-12-21 2015-04-08 株式会社ヴァレオジャパン スクロール型圧縮機

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JPH09126161A (ja) * 1995-11-08 1997-05-13 Hitachi Ltd スクロール圧縮機
WO2016056172A1 (fr) * 2014-10-07 2016-04-14 パナソニックＩｐマネジメント株式会社 Compresseur à spirales
JP2017115762A (ja) * 2015-12-25 2017-06-29 サンデンホールディングス株式会社 スクロール型圧縮機

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Publication number Priority date Publication date Assignee Title
JPWO2022050142A1 (fr) * 2020-09-02 2022-03-10
WO2022050142A1 (fr) * 2020-09-02 2022-03-10 三菱電機株式会社 Compresseur à spirale
GB2612265A (en) * 2020-09-02 2023-04-26 Mitsubishi Electric Corp Scroll compressor
JP7321384B2 (ja) 2020-09-02 2023-08-04 三菱電機株式会社 スクロール圧縮機
GB2612265B (en) * 2020-09-02 2024-05-15 Mitsubishi Electric Corp Scroll compressor
WO2022102564A1 (fr) * 2020-11-10 2022-05-19 三菱電機株式会社 Compresseur à spirale et procédé d'assemblage de compresseur à spirale
GB2614015A (en) * 2020-11-10 2023-06-21 Mitsubishi Electric Corp Scroll compressor and method for assembling scroll compressor
JP7450753B2 (ja) 2020-11-10 2024-03-15 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組立方法

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JPWO2019207759A1 (ja) 2021-02-12
CN112005012B (zh) 2022-07-12
CN112005012A (zh) 2020-11-27
JP7076536B2 (ja) 2022-05-27

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