EP4242462A1 - Compresseur rotatif - Google Patents

Compresseur rotatif Download PDF

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Publication number
EP4242462A1
EP4242462A1 EP21903371.9A EP21903371A EP4242462A1 EP 4242462 A1 EP4242462 A1 EP 4242462A1 EP 21903371 A EP21903371 A EP 21903371A EP 4242462 A1 EP4242462 A1 EP 4242462A1
Authority
EP
European Patent Office
Prior art keywords
cylinder
bearing
rotary compressor
compression mechanism
drive shaft
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
EP21903371.9A
Other languages
German (de)
English (en)
Other versions
EP4242462A4 (fr
Inventor
Fumiya HAMAGUCHI
Kana Sakon
Ryoji OKABE
Hitoshi Tamaki
Takuma YAMASHITA
Norihisa Horaguchi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsubishi Heavy Industries Thermal Systems Ltd
Original Assignee
Mitsubishi Heavy Industries Thermal Systems Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Mitsubishi Heavy Industries Thermal Systems Ltd filed Critical Mitsubishi Heavy Industries Thermal Systems Ltd
Publication of EP4242462A1 publication Critical patent/EP4242462A1/fr
Publication of EP4242462A4 publication Critical patent/EP4242462A4/fr
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/10—Outer members for co-operation with rotary pistons; Casings
    • F01C21/104—Stators; Members defining the outer boundaries of the working chamber
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/356—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member
    • F04C18/3562—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation
    • F04C18/3564—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the outer member the inner and outer member being in contact along one line or continuous surfaces substantially parallel to the axis of rotation the surfaces of the inner and outer member, forming the working space, being surfaces of revolution
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/30—Casings or housings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2240/00—Components
    • F04C2240/80—Other components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2270/00—Control; Monitoring or safety arrangements
    • F04C2270/16—Wear
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05C—INDEXING SCHEME RELATING TO MATERIALS, MATERIAL PROPERTIES OR MATERIAL CHARACTERISTICS FOR MACHINES, ENGINES OR PUMPS OTHER THAN NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES
    • F05C2253/00—Other material characteristics; Treatment of material
    • F05C2253/04—Composite, e.g. fibre-reinforced

Definitions

  • the present disclosure relates to a rotary compressor.
  • Patent Document 1 discloses a rotary compressor including a motor accommodated in a hermetic container, a rotary compression mechanism driven by the motor, and a drive shaft that transmits a driving force of the motor to the compression mechanism.
  • the rotary compression mechanism compresses a refrigerant by causing a roller connected to the drive shaft to rotate in a cylinder chamber.
  • the cylinder chamber is defined by a cylinder main body, bearings disposed above and below the cylinder main body for supporting the drive shaft, and a separator.
  • Patent Document 1 JP 2016-160911 A
  • each member may be damaged or noise may be generated when a rotor rotationally moving in the cylinder chamber comes into contact with the bearing and/or the like.
  • the bearing and/or the like need(s) to be manufactured with high accuracy, which makes it difficult to manufacture the bearing and/or the like.
  • the present disclosure has been made in view of such circumstances, and an object thereof is to provide a rotary compressor that can facilitate a process of manufacturing a bearing or the like.
  • a rotary compressor of the present disclosure employs the following means.
  • a rotary compressor includes a housing that forms an outer shell, a drive source, a compression mechanism accommodated in the hermetic housing and configured to compress a refrigerant by using a driving force from the drive source, and a drive shaft connecting the drive source and the compression mechanism and configured to rotate about a center axis extending in a predetermined direction.
  • the compression mechanism includes a rotor connected to the drive shaft and accommodated in a cylinder chamber, a cylinder defining an outer side of the cylinder chamber in a radial direction, and a bearing rotatably supporting the drive shaft and defining the cylinder chamber in the predetermined direction.
  • the refrigerant is compressed between the rotor being rotated and the cylinder.
  • the bearing and/or the cylinder are/is formed of a composite material made by reinforcing a resin with reinforced fibers.
  • a process of manufacturing a bearing and/or the like can be facilitated.
  • a rotary compressor 1 includes a hermetic housing (case) 2 having a cylindrical shape that forms an outer shell. An upper portion and a lower portion of the hermetic housing 2 are hermetically sealed by covers 3 and 4, respectively. An electric motor 5 is disposed at an upper portion of the hermetic housing 2, and a compression mechanism 6 driven by the electric motor (drive source) 5 is disposed at a lower portion of the hermetic housing 2.
  • the rotary compressor 1 is an electric compressor having a hermetic structure.
  • a plurality of mounting brackets 7 are provided on an outer periphery of the lower portion of the hermetic housing 2, and a discharge pipe 8 is disposed at the upper portion of the hermetic housing 2 penetrating the upper cover 3, so that a high-pressure refrigerant gas compressed by the compression mechanism 6 and discharged into the hermetic housing 2 can be delivered to the outside of the compressor (refrigeration cycle).
  • An accumulator (not illustrated) is integrally assembled to an outer peripheral portion of the hermetic housing 2.
  • the accumulator separates a liquid portion such as oil and liquid coolant contained in a low-pressure refrigerant gas returned from the refrigeration cycle so that only a gas portion is sucked into the compression mechanism 6 via a suction pipe 10.
  • the electric motor 5 includes a stationary element 12 and a rotating element 13, and the stationary element 12 is fixed and disposed at an inside surface of the hermetic housing 2 by shrink fitting, press fitting, or the like.
  • the rotating element 13 is integrally joined to a drive shaft 14, and a rotational driving force of the rotating element 13 can be transmitted to the compression mechanism 6 via the drive shaft 14.
  • an upper eccentric portion 15 and a lower eccentric portion 16 are disposed at two upper and lower positions at a predetermined interval in an axial direction with a phase shift of 180 degrees, corresponding to an upper compression mechanism 30 and a lower compression mechanism 60 of the compression mechanism 6 to be described later.
  • the drive shaft 14 is a substantially cylindrical member and is disposed such that a center axis thereof extends in the vertical direction.
  • the drive shaft 14 connects the electric motor 5 and the compression mechanism 6.
  • the drive shaft 14 rotates about the center axis by the driving force of the electric motor 5.
  • the compression mechanism 6 is a two-cylinder type rotary compression mechanism including the upper compression mechanism 30 and the lower compression mechanism 60.
  • the compression mechanism 6 also includes a separator plate (separator) 50 disposed between the upper compression mechanism 30 and the lower compression mechanism 60.
  • separator plate separator 50 disposed between the upper compression mechanism 30 and the lower compression mechanism 60.
  • radial direction means a radial direction with reference to the center axis of the drive shaft 14.
  • the upper compression mechanism 30 includes, in the interior of the upper compression mechanism 30, an upper bearing cylinder portion 32 that defines an upper cylinder chamber (cylinder chamber) 31, and an upper rotor (rotor) 33 connected to the drive shaft 14 and accommodated in the upper cylinder chamber 31.
  • the upper bearing cylinder portion 32 includes an upper cylinder main portion 34 (cylinder) that defines an outer side of the upper cylinder chamber 31 in the radial direction, and an upper bearing portion (bearing) 35 that rotatably supports the drive shaft 14 and defines an upper side of the upper cylinder chamber 31. That is, the upper cylinder main portion 34 and the upper bearing portion 35 are integrally formed.
  • the upper bearing cylinder portion 32 is entirely formed of a composite material made by reinforcing a resin with short fibers (hereinafter referred to as a "short fiber composite material").
  • the short fibers are, for example, glass fibers or carbon fibers having a fiber length of about 0. 1 mm to several millimeters.
  • integrally formed does not mean that the upper bearing portion 35 and the upper cylinder main portion 34 are formed as separate members and then fixed to each other by a fastener, welding, or the like to be integrated with each other, but means that the upper bearing portion 35 and the upper cylinder main portion 34 are formed of the same material and thereby integrated with each other without a joint or the like.
  • the upper bearing portion 35 and the upper cylinder main portion 34 of the upper bearing cylinder portion 32 are integrally formed by injection molding.
  • the method of forming the upper bearing cylinder portion 32 is only an example and is not limited to injection molding.
  • the upper bearing portion 35 rotatably supports the drive shaft 14.
  • the upper bearing portion 35 integrally includes a cylindrical portion 35a into which the drive shaft 14 is inserted, a plurality of ribs 35b each having a plate shape and projecting in the radial direction from an outside surface of the cylindrical portion 35a, and an annular portion 35c having a plate shape and extending in the radial direction from a lower end of the cylindrical portion 35a.
  • the cylindrical portion 35a, the ribs 35b, and the annular portion 35c have substantially the same thickness.
  • the cylindrical portion 35a is disposed such that the center axis thereof coincides with the center axis of the drive shaft 14. As illustrated in FIG. 4 , a step part with a varying inside diameter is formed at an inside surface of the cylindrical portion 35a.
  • Two metal bushings (bearing wear-resistant portions) 36 are disposed inside the cylindrical portion 35a in contact with the step part. Note that the metal bushings 36 are omitted in FIGS. 1 to 3 for convenience of illustration.
  • the metal bushings 36 are disposed between the cylindrical portion 35a and the drive shaft 14.
  • each metal bushing 36 is a cylindrical member.
  • the metal bushing 36 is formed of a metal material (e.g., cast iron, an aluminum alloy, or a copper alloy).
  • Two notch portions 36a recessed inward in the radial direction are formed in an outside surface of the metal bushing 36.
  • the two notch portions 36a are disposed at equal intervals in the circumferential direction.
  • Each notch portion 36a is formed extending from one end of the metal bushing 36 in the vertical direction to a central portion of the metal bushing 36.
  • a stopper portion 36b having a planar shape is disposed at the other end of each notch portion 36b in the vertical direction.
  • the cylindrical portion 35a includes an engaging portion (not illustrated) that engages with the notch portion 36a.
  • Rotation of the metal bushing 36 can be restricted by the engagement between the notch portion 36a and the engaging portion.
  • movement of the metal bushing 36 in the vertical direction is restricted by the contact between the engaging portion and the stopper portion 36b, and thus removal of the metal bushing 36 from the cylindrical portion 35a can be prevented.
  • the metal bushing 36 is disposed at upper and lower portions of the cylindrical portion 35a. That is, the metal bushing 36 is not disposed at a central portion of the cylindrical portion 35a.
  • the length in the vertical direction of a region where the metal bushing 36 is not disposed is set to be 20% to 30% of the length in the vertical direction of the cylindrical portion 35a. Note that the length of the region where the metal bushing 36 is not disposed is only an example, and is not limited to the above-described numerical values.
  • the metal bushing 36 can be integrally molded with a bearing cylinder portion by being set in a mold before resin is injected. Manufacturing costs can be reduced by the integral molding described above.
  • the plurality of ribs 35b are arranged side by side in the circumferential direction of the cylindrical portion 35a so as not to be largely biased.
  • Each rib 35b protrudes from an outside surface of the cylindrical portion 35a substantially over the entire range of the cylindrical portion 35a in the vertical direction.
  • Each rib 35b is formed to protrude longer toward the lower side.
  • a lower end of each rib 35b is connected to an upper surface of the annular portion 35c.
  • An outer end in the radial direction of a lower portion of each rib 35b is connected to an inside surface of an outer frame portion 34c of the upper cylinder main portion 34 to be described later.
  • Each rib 35b has a shape in which a substantially triangular member is connected to the top of a substantially rectangular member in a side view.
  • a side surface (a surface intersecting a plate surface) of the rectangular member and a side surface of the triangular member are smoothly connected to each other such that a connected portion forms a curved surface.
  • junction portion 37 is connected to a predetermined rib 35b.
  • the junction portion 37 defines a first bolt hole 37a (screw hole) into which a bolt 38 is inserted.
  • first bolt hole 37a is formed on a predetermined rib 35b.
  • a plurality of junction portions 37 are formed.
  • the first bolt hole 37a extends through the upper bearing cylinder portion 32.
  • the first bolt hole 37a communicates with a second bolt hole 52 formed in a separator plate 50 to be described later.
  • the upper bearing cylinder portion 32 and the separator plate 50 are screwed and fixed to each other by the bolts 38 inserted into the first bolt holes 37a and the second bolt holes 52.
  • the annular portion 35c is an annular member having an opening formed at a substantially central portion thereof, and the drive shaft 14 is to be inserted through the opening.
  • the annular portion 35c defines an upper side of the upper cylinder chamber 31 and defines an upper side of a second flow path 42 formed in the upper cylinder main portion 34 to be described later.
  • FIGS. 6 to 9 the upper cylinder main portion 34 is illustrated upside down for convenience of explanation. That is, in FIGS. 6 to 9 , the lower side of the drawing corresponds to the vertically upper side, and the upper side of the drawing corresponds to the vertically lower side.
  • the upper cylinder main portion 34 integrally includes a defining portion 34a having a cylindrical shape that defines an outer side of the upper cylinder chamber 31 in the radial direction, a contact portion 34b having a plate shape and extending outward in the radial direction from a lower end of the defining portion 34a, and the outer frame portion 34c having a cylindrical shape, being bent at a substantially right angle from an outer end portion of the contact portion 34b in the radial direction, and extending upward from the outer end portion.
  • the defining portion 34a, the contact portion 34b, and the outer frame portion 34c have substantially the same thickness.
  • the plate thicknesses of the defining portion 34a and the like of the upper cylinder main portion 34 is substantially the same as the plate thicknesses of the ribs 35b and the like of the upper bearing portion 35.
  • An inside surface of the defining portion 34a defines the upper cylinder chamber 31.
  • An upper end of the defining portion 34a is connected to a bottom surface of an outer end portion of the annular portion 35c in the radial direction.
  • a suction port 43 is formed in the defining portion 34a. The suction port 43 opens to the upper cylinder chamber 31.
  • a bottom surface of the contact portion 34b is in contact with a top surface of the separator plate 50.
  • the junction portions 37 are formed in a top surface of the contact portion 34b.
  • the outer frame portion 34c is disposed outside the defining portion 34a in the radial direction.
  • the outer frame portion 34c stands so as to face the defining portion 34a.
  • a second flow path 42 is formed between the defining portion 34a and the outer frame portion 34c, and the second flow path 42 is connected to a first flow path 41 formed in the separator plate 50, which will be described later.
  • the second flow path 42 is a flow path having a substantially circular flow path cross-section extending in the vertical direction.
  • a downstream end portion of the second flow path 42 is connected to the suction port 43 (suction port) formed in the defining portion 34a. Accordingly, a refrigerant flowing through the second flow path 42 flows into the upper cylinder chamber 31 via the suction port 43.
  • the suction port 43 is formed in a rectangular shape. Specifically, the suction port 43 has a rectangular shape in which a length in the vertical direction is longer than a length in a direction intersecting the vertical direction (that is, a rotational direction of the upper rotor 33).
  • An upper edge of the suction port 43 is defined by the upper bearing portion 35 and a lower edge thereof is defined by the separator.
  • An edge of the suction port 43 in the rotational direction is defined by the defining portion 34a.
  • the upper cylinder main portion 34 includes a blade (not illustrated) that partitions the upper cylinder chamber 31 into a suction side and a discharge side for a refrigerant, and a blade groove 44 that slidably accommodates the blade.
  • the blade is formed of a metal material.
  • the blade is slidably fitted in the blade groove 44.
  • the blade groove 44 is a groove extending in the radial direction and accommodates the blade.
  • An inner end of the blade groove 44 in the radial direction is connected to the upper cylinder chamber 31.
  • the blade groove 44 is disposed adjacent to the suction port 43.
  • an end portion on the cylinder chamber side (an inner end portion in the radial direction) of a side wall surface of the blade groove 44 on the suction side (suction port 43 side) is entirely covered by a suction-side wear-resistant portion 45 in the vertical direction.
  • a side wall surface of the blade groove 44 on the discharge side is covered by a discharge-side wear-resistant portion 46 over substantially the entire range in the radial direction.
  • the suction-side wear-resistant portion 45 and the discharge-side wear-resistant portion 46 are formed of a metal material (e.g., cast iron, an aluminum alloy, or a copper alloy).
  • the suction-side wear-resistant portion 45 and the discharge-side wear-resistant portion 46 include, at outer end portions thereof in the radial direction, protrusions 45a and 46a, respectively, that engage with recesses 45b and 46b of the upper cylinder main portion 34, respectively. With the engagement between the protrusions 45a and 46a and the recesses 45b and 46b, the suction-side wear-resistant portion 45 and the discharge-side wear-resistant portion 46 can be restricted from moving in the radial direction. Note that, in FIG. 6 , the suction-side wear-resistant portion 45 and the discharge-side wear-resistant portion 46 are omitted for convenience of illustration.
  • the present disclosure is not limited thereto.
  • the side wall surface of the blade groove 44 on the suction side may be covered by the suction-side wear-resistant portion 45 over substantially the entire range in the radial direction.
  • these wear-resistant portions can be integrated and the manufacturing cost thereof can be reduced.
  • the upper rotor 33 is fitted to an outside surface of the upper eccentric portion 15.
  • the center axis of the upper eccentric portion 15 is eccentric with respect to the center axis of the drive shaft 14.
  • the upper rotor 33 revolves in the upper cylinder chamber 31 together with the rotation of the drive shaft 14.
  • a refrigerant is compressed between the revolving upper rotor 33 and the upper cylinder main portion 34.
  • the separator plate 50 is a plate-like member formed of a metal material (e.g., cast iron). As illustrated in FIG. 10 , the separator plate 50 is an annular member having an opening formed in a central portion thereof, and the drive shaft 14 is inserted into the opening. The separator plate 50 is fixed to an inside surface of the hermetic housing 2 by plug welding, caulking, or the like.
  • a metal material e.g., cast iron
  • the separator plate 50 separates the upper cylinder chamber 31 and a lower cylinder chamber.
  • a top surface of the separator plate 50 defines a bottom side of the upper cylinder chamber 31.
  • a bottom surface of the separator plate 50 defines a top side of the lower cylinder chamber.
  • a suction pipe insertion hole is formed in the separator plate 50 extending inward in the radial direction from a side surface of the separator plate 50.
  • the suction pipe 10 that guides a refrigerant to the upper cylinder chamber 31 is inserted into the suction pipe insertion hole.
  • the first flow path 41 is formed in the separator plate 50, extending through the separator plate 50 in the vertical direction.
  • An upstream end of the first flow path 41 is connected to the suction pipe 10.
  • a downstream end of the first flow path 41 is connected to an upstream end of the second flow path 42.
  • the first flow path 41 and the second flow path 42 are connected to each other to form a single linear flow path extending in the vertical direction.
  • the second bolt hole 52 communicating with the first bolt hole 37a is formed in the separator plate 50.
  • the inside surface of the second bolt hole 52 is formed with a female thread that mates with a male thread of the bolt 38.
  • the upper bearing cylinder portion 32 and the separator plate 50 are screwed and fixed to each other by the bolts 38 inserted into the first bolt holes 37a and the second bolt holes 52.
  • the lower compression mechanism 60 has a structure vertically symmetrical to the upper compression mechanism 30 with respect to the separator plate 50. Thus, a detailed description of the lower compression mechanism 60 will be omitted.
  • the refrigerant compressed in the upper cylinder chamber 31 and the lower cylinder chamber is discharged into a discharge chamber (not illustrated) via a discharge port (not illustrated) and a discharge valve (not illustrated), discharged from the discharge chamber into the hermetic housing 2, and then guided to an upper portion of the hermetic housing 2 to be discharged to the refrigeration cycle side via the discharge pipe 8.
  • the following operational effects are obtained.
  • the effects of the upper compression mechanism 30 will be mainly described below, but, as a matter of course, the same effects as those of the upper compression mechanism 30 can also be obtained in the lower compression mechanism 60.
  • the upper bearing cylinder portion 32 defining the upper cylinder chamber 31 is formed of a short fiber composite material.
  • the short fiber composite material is more likely to deform than a metal material or the like.
  • the upper bearing cylinder portion 32 since the deformation of the upper bearing cylinder portion 32 is caused by the contact with the upper rotor 33, the upper bearing cylinder portion 32 does not deform to such an extent that a gap formed between the upper bearing cylinder portion 32 and the upper rotor 33 becomes excessively large.
  • the contact between the upper bearing cylinder portion 32 and the upper rotor 33 can be reduced without strictly managing the gap formed between the upper bearing cylinder portion 32 and the upper rotor 33 in manufacturing the upper compression mechanism 30. Accordingly, the compression mechanism 6 can be manufactured more easily.
  • the deformation of the upper bearing cylinder portion 32 includes deformation caused by the upper rotor 33 or the like cutting the upper bearing cylinder portion 32.
  • the bearing is formed of a metal material
  • the drive shaft 14 comes into one-sided contact with the bearing, a local surface pressure may increase, and the reliability of the bearing may be decreased.
  • the upper bearing cylinder portion 32 is formed of a composite material, the upper bearing cylinder portion 32 deforms in accordance with the deformation of the drive shaft 14. Accordingly, the increase in the local surface pressure of the upper bearing cylinder portion 32 can be suppressed and the decrease in the reliability of the bearing function of the upper bearing portion 35 can be suppressed.
  • the bearing and the cylinder are formed of a metal material
  • the bearing and/or the like are/is formed by machining, interference with a tool or the like needs to be considered, and thus the forming operation may become complicated.
  • the forming operation may become further complicated.
  • the bearing and the cylinder are formed of a composite material.
  • the bearing and/or the like can be molded by injection molding or the like using a mold or the like, and thus no complicated work such as machining is needed.
  • a member having a complicated shape such as the upper bearing cylinder portion 32 in which the bearing and the cylinder are integrally formed can be easily molded.
  • the bearing and the cylinder are integrally formed, the number of components can be reduced as compared to a case where the bearing and the cylinder are separate bodies. Accordingly, costs and time required for assembly work can be reduced.
  • the bearing and the cylinder when the bearing and the cylinder are formed as separate bodies, the bearing and the cylinder need to be aligned so as to be coaxial with each other. However, when the bearing and the cylinder are integrally formed, alignment of the bearing and the cylinder can be eliminated.
  • the bearing and the cylinder are integrally formed, by supporting the drive shaft 14 by the bearing, the position of the upper rotor 33 in the upper cylinder chamber 31 is also determined. As a result, variations in the gap formed between the upper cylinder portion and the upper rotor 33 can be reduced. Accordingly, fitting based on the actual dimensions of the cylinder and the bearing can be eliminated.
  • the upper bearing cylinder portion 32 is fixed to the separator plate 50, and the separator plate 50 is fixed to the hermetic housing 2. Accordingly, the drive shaft 14 is supported by the hermetic housing 2 via the upper bearing cylinder portion 32 and the separator plate 50.
  • the separator plate 50 is formed of a metal material. A metal material is less likely to deform than a composite material or the like. As described above, since the drive shaft 14 is supported by the separator plate 50 formed of a metal material, which is less likely to deform, the drive shaft 14 can be made less likely to topple as compared to a case where the separator plate 50 is formed of a short fiber composite material. Accordingly, the contact between the rotating element 13 and the stationary element 12 due to the deformation of the drive shaft 14 can be made less likely to occur.
  • the compression mechanism 6 is fixed to the hermetic housing 2 by the separator plate 50 located at a central portion in the vertical direction.
  • the separator plate 50 located at a central portion in the vertical direction.
  • the suction pipe 10 is connected to the separator plate 50 made of a metal material.
  • the separator plate 50 made of a metal material.
  • the suction pipe 10 is connected to the separator plate 50.
  • the number of suction pipes 10 can be reduced as compared to a case where a plurality of suction pipes 10 connected to the respective cylinder chambers are provided. Accordingly, the number of components can be reduced, and thus costs and time required for assembly work can be reduced.
  • an upper edge of the suction port 43 is defined by the upper bearing cylinder portion 32 and a lower edge of the suction port 43 is defined by the separator plate 50. That is, when only the upper bearing cylinder portion 32 is viewed, the lower side of the suction port 43 is opened.
  • a length of the suction port 43 in the vertical direction can be increased as compared to a case where a member for closing the lower side of the suction port 43 is provided, and thus the area of the suction port 43 can be increased accordingly.
  • a length of the suction port 43 in a direction intersecting a predetermined direction i.e., the rotational direction of the upper rotor 33
  • a time during which the suction port 43 is closed by the upper rotor 33 can be increased, and thus the compression efficiency for the refrigerant in the upper cylinder chamber 31 can be improved.
  • the upper bearing cylinder portion 32 since the lower side of the suction port 43 is opened in the upper bearing cylinder portion 32, when the upper bearing cylinder portion 32 is formed by injection molding and is removed upward from the mold, the upper bearing cylinder can be easily removed from the mold.
  • the junction portions 37 are connected to the corresponding ribs 35b.
  • a load acting on the upper bearing portion 35 when the drive shaft 14 is about to incline can be transmitted to the separator plate 50 via the ribs 35b and the junction portions 37. Accordingly, since the drive shaft 14 can be supported by the separator plate 50 that is less likely to deform, deformation of the drive shaft 14 can be reduced.
  • the rib 35b is a plate-like member having a constant plate thickness and extends in the radial direction from an outside surface of the cylindrical portion 35a of the upper bearing portion 35.
  • a length (plate thickness) of the rib 35b in the circumferential direction is constant. Accordingly, for example, when the upper bearing cylinder portion 32 is formed by injection molding and is removed upward from the mold, the rib 35b and the mold do not interfere with each other, and thus the upper bearing cylinder portion 32 can be easily removed from the mold.
  • the plurality of ribs 35b are arranged at equal intervals in the circumferential direction of the cylindrical portion 35a.
  • the rigidity of the cylindrical portion 35a in the inclination direction can be improved over the entire range in the circumferential direction.
  • thermal expansion or shrinkage of the upper bearing portion 35 is absorbed by the ribs 35b.
  • inclination of the drive shaft 14 due to thermal expansion or shrinkage of the upper bearing portion 35 can be reduced.
  • the ribs 35b function as inflow paths of the short fiber composite material. Accordingly, the composite material can easily and uniformly flow throughout the entire upper bearing cylinder portion 32.
  • each fiber contained in the short fiber composite material extends along an inflow direction. Since the inflow direction is substantially the same as the inclination direction of the drive shaft 14, rigidity with respect to the inclination direction of the drive shaft 14 can be improved.
  • the metal bushing 36 is disposed between the upper bearing portion 35 and the drive shaft 14. This improves a limit PV value, and thus the wear of the upper bearing portion 35 due to the rotation of the drive shaft 14 can be reduced.
  • the metal bushing 36 is disposed at both end portions of the upper bearing portion 35 in the vertical direction. That is, the metal bushing 36 is not disposed at a central portion of the upper bearing portion 35.
  • the upper bearing portion 35 is more likely to deform in response to the deformation of the drive shaft 14 as compared to a case where the metal bushing 36 is disposed over substantially the entire range of the upper bearing portion 35 in the vertical direction. That is, the metal bushings 36 are unlikely to restrict the deformation of the upper bearing portion 35. Since the upper bearing portion 35 deforms in response to the deformation of the drive shaft 14, even when the drive shaft 14 deforms, a surface pressure acting on the upper bearing portion 35 can be reduced, and thus the wear of the upper bearing portion 35 can be reduced.
  • the manufacturing cost of the metal bushing 36 can be reduced.
  • the suction-side wear-resistant portion 45 and the discharge-side wear-resistant portion 46 are disposed at the end portions of the blade groove 44 on the upper cylinder chamber 31 side.
  • the wear of the upper cylinder main portion 34 due to the sliding of the blade can be reduced.
  • the suction-side wear-resistant portion 45 only the inner end portion in the radial direction of the side wall surface of the blade groove 44 on the suction side is covered by the suction-side wear-resistant portion 45.
  • the upper cylinder portion is more likely to deform in response to a load from the blade as compared to a case where the wear-resistant portion is disposed over substantially the entire range of the cylinder groove. That is, the suction-side wear-resistant portion 45 is unlikely to restrict the deformation of the upper cylinder portion. Since the upper cylinder portion deforms responding to a load from the blade, a surface pressure acting on the upper cylinder portion can be reduced, and thus the wear of the upper cylinder portion can be reduced.
  • the volume of the suction-side wear-resistant portion 45 is reduced as compared to a case where the wear-resistant portion is disposed over substantially the entire range of the blade groove 44, and thus the manufacturing cost of the suction-side wear-resistant portion 45 can be reduced.
  • the wear since the blade mainly comes into contact with only the inner end portion of the side wall surface on the suction side in the radial direction, the wear can be suitably reduced even though the wear-resistant portion covers only the inner end portion.
  • a sleeve 65 may be disposed between the bolt 38 and the inside surface of the junction portion 37.
  • the sleeve 65 is formed of a metal material (e.g., cast iron, an aluminum alloy, or a copper alloy).
  • the sleeve 65 is disposed from the upper end of the junction portion 37 to a position above a lower end of the junction portion 37. That is, the sleeve 65 is not disposed up to the lower end of the junction portion 37. Thus, the sealing performance between the bolt 38 and the junction portion 37 can be increased as compared to a case where the sleeve 65 is disposed up to the lower end of the junction portion 37.
  • the bolt 38 may be formed of aluminum.
  • Aluminum has a linear expansion coefficient closer to the linear expansion coefficient of the short fiber composite material than iron.
  • a creep phenomenon can be suppressed as compared to a case where the bolt 38 is formed of iron.
  • an excess thickness portion 66 may be disposed on the outer side in the radial direction of the suction port 43 of the upper bearing cylinder portion 32, protruding further outward in the radial direction than other regions.
  • a low-temperature refrigerant before compression is guided into the suction port 43.
  • the temperature of a region near the suction port 43 is lower than the temperatures of other regions.
  • the thermal expansion coefficient of the short fiber composite material is larger than that of metal or the like.
  • a region near the suction port 43 may deform due to a difference in temperature with other regions.
  • the adhesion between the upper bearing cylinder portion 32 and the separator plate 50 is reduced, and thus the refrigerant may leak from the upper cylinder chamber 31.
  • the upper bearing cylinder portion 32 is provided with the excess thickness portion 66 on the outer side of the suction port 43 in the radial direction.
  • the excess thickness portion 66 With the excess thickness portion 66, a region near the suction port 43 is less likely to deform. Accordingly, the deformation of the upper bearing cylinder portion 32 can be suppressed, and thus leakage of the refrigerant from the upper cylinder chamber 31 can be suppressed.
  • a rotary compressor 70 of a so-called single-cylinder type in which only one cylinder is provided is conceivable.
  • a compression mechanism 71 includes an upper bearing 72, a lower bearing 73, and a cylinder main body portion 74.
  • the upper bearing 72, the lower bearing 73, and the cylinder main body portion 74 are formed as separate bodies.
  • the upper bearing 72 and/or the lower bearing 73 are/is formed of a short fiber composite material.
  • the cylinder main body portion 74 is formed of a metal material.
  • the cylinder main body portion 74 is fixed to the hermetic housing 2.
  • the upper bearing 72 and the cylinder main body portion 74 are screwed and fixed to each other by a bolt 75.
  • the lower bearing 73 and the cylinder main body portion 74 are also screwed and fixed to each other by a bolt 76.
  • the upper bearing 72 and the cylinder main body portion 74 may be integrally formed of a composite material.
  • the lower bearing 73 is formed of a metal material, and the lower bearing 73 is fixed to the hermetic housing 2.
  • the lower bearing 73 and the cylinder main body portion 74 may be integrally formed of a composite material.
  • the upper bearing 72 is formed of a metal material, and the upper bearing 72 is fixed to the hermetic housing 2.
  • a rotary compressor includes a hermetic housing (2) that forms an outer shell, a drive source (5), a compression mechanism (6) accommodated in the hermetic housing and configured to compress a refrigerant by using a driving force from the drive source, and a drive shaft (14) connecting the drive source and the compression mechanism and configured to rotate about a center axis extending in a predetermined direction.
  • the compression mechanism includes a rotor (33) connected to the drive shaft and accommodated in a cylinder chamber (31), a cylinder (34) defining an outer side of the cylinder chamber in a radial direction, and a bearing (35) rotatably supporting the drive shaft and defining the cylinder chamber in the predetermined direction.
  • the compression mechanism compresses the refrigerant between the rotor being rotated and the cylinder.
  • the bearing and/or the cylinder are/is formed of a composite material made by reinforcing a resin with reinforced fibers.
  • the bearing and/or the cylinder (hereinafter referred to as "bearing and/or the like") defining the cylinder chamber are/is formed of a composite material obtained by reinforcing a resin with reinforced fibers.
  • the composite material is more likely to deform than another material such as a metal material.
  • the contact between the bearing and/or the like and the rotor can be reduced.
  • the bearing and/or the like does not deform to such an extent that a gap formed between the bearing and/or the like and the rotor becomes excessively large.
  • the contact between the bearing and/or the like and the rotor can be reduced without strictly managing the gap formed between the bearing and/or the like and the rotor in manufacturing the compression mechanism. Accordingly, manufacturing of the compression mechanism can be facilitated.
  • the deformation of the bearing and/or the like includes deformation caused by the rotor cutting the bearing and/or the like.
  • the bearing and the cylinder are formed of the composite material, and the bearing and the cylinder are integrally formed.
  • the bearing and the cylinder are formed of a metal material
  • the bearing and/or the like are/is formed by machining, interference with a tool or the like needs to be considered, and thus the forming operation may become complicated.
  • the forming operation may become further complicated.
  • the bearing and the cylinder are formed of the composite material.
  • the bearing and/or the like can be molded by injection molding or the like using a mold or the like, and thus no complicated work such as machining is needed.
  • a member having a complicated shape in which the bearing and the cylinder are integrated can be easily molded.
  • the bearing and the cylinder are integrally formed, the number of components can be reduced as compared to a case where the bearing and the cylinder are separate bodies. Accordingly, costs and time required for assembly work can be reduced.
  • the bearing and the cylinder when the bearing and the cylinder are formed as separate bodies, the bearing and the cylinder need to be aligned so as to be coaxial with each other. However, when the bearing and the cylinder are integrally formed, alignment of the bearing and the cylinder can be eliminated.
  • integral formed does not mean that the bearing and the cylinder are formed as separate members and then fixed to each other by a fastener, welding, or the like, but means that the bearing and the cylinder are formed integrated with each other by, for example, injection molding.
  • the drive source includes a rotating element (13) fixed to the drive shaft and a stationary element (12) surrounding the rotating element
  • the compression mechanism includes a plurality of the cylinder chambers arranged in the predetermined direction and a plurality of the rotors respectively accommodated in the cylinder chambers, the cylinder chambers adjacent to each other in the predetermined direction are separated by a separator (50), the bearing and the cylinder integrally formed are fixed to the separator, and the separator is formed of a metal material and fixed to the housing.
  • the bearing is fixed to the separator, and the separator is fixed to the housing.
  • the drive shaft is fixed to the housing via the bearing and the separator formed of a metal material.
  • the separator is formed of a metal material. A metal material is less likely to deform than a composite material or the like.
  • the drive shaft can be made less likely to deform as compared to a case where the separator is formed of a composite material. Accordingly, the rotating element and the stationary element can be made less likely to come into contact with each other due to the deformation of the drive shaft.
  • the compression mechanism is fixed to the housing by the separator located at a relatively central portion in the predetermined direction.
  • a distance from a point of fixing to the housing to each cylinder chamber in which the refrigerant is compressed is shorter. Accordingly, the deformation of the bearing, the cylinder, or the like can be reduced.
  • a rotary compressor further includes a suction pipe (10) that guides the refrigerant to the compression mechanism, in which the suction pipe is connected to the separator, and the compression mechanism includes a refrigerant flow path (41, 42) that guides the refrigerant supplied from the suction pipe to the cylinder chamber.
  • the suction pipe is connected to the separator made of a metal material.
  • the connected member the separator
  • heat generated during connection of the suction pipe e.g., heat associated with brazing or welding
  • the suction pipe is connected to the separator.
  • the number of suction pipes can be reduced as compared to a case where a plurality of suction pipes respectively connected to the cylinder chambers are provided. Accordingly, the number of components can be reduced, and thus costs and time required for assembly work can be reduced.
  • the refrigerant flow path includes a downstream end portion connected to a suction port (43) opening to the cylinder chamber, and one side of the suction port in the predetermined direction is defined by the bearing and an other side of the suction port in the predetermined direction is defined by the separator.
  • the one side of the suction port in the predetermined direction is defined by the bearing, and the other side of the suction port in the predetermined direction is defined by the separator. That is, when only an integrated body of the bearing and the cylinder is viewed, the other side of the suction port in the predetermined direction is open. Accordingly, a length of the suction port in the predetermined direction can be increased as compared to a case where a member for closing the other side of the suction port is provided, and thus the area of the suction port can be increased.
  • a length of the suction port in a direction intersecting the predetermined direction i.e., a rotational direction of the rotor
  • a time during which the suction port is closed by the rotor can be increased, and thus the compression efficiency for the refrigerant in the cylinder chamber can be improved.
  • the other side of the suction port in the predetermined direction is opened in the integrated body of the bearing and the cylinder, for example, when the bearing and the cylinder are integrally formed by injection molding and are removed in a direction toward the one side in the predetermined direction from a mold, the bearing and the cylinder can be easily removed from the mold.
  • a rotary compressor according to an aspect of the present disclosure further includes a screw member (38) configured to fix the bearing and the cylinder integrally formed and the separator, in which the bearing and the cylinder integrally formed include a rib (35b) that reinforces the bearing and a junction portion (37) defining a screw hole through which the screw member is inserted, and the junction portion is connected to the rib.
  • the junction portion is connected to the rib.
  • a load acting on the bearing when the drive shaft is about to incline can be transmitted to the separator plate via the rib and screw member. Accordingly, the drive shaft can be supported by the separator plate that is less likely to deform, and thus deformation of the drive shaft can be reduced.
  • a sleeve (65) formed of a metal material is disposed between an inside surface of the screw hole and the screw member.
  • the sleeve formed of a metal material is disposed between the inside surface of the screw hole and the screw member. Accordingly, a creep phenomenon can be suppressed, and thus a decrease in the axial force of the screw member can be suppressed.
  • the rib is a plate-like member having a constant plate thickness and extends in a radial direction from an outside surface of the bearing having a cylindrical shape.
  • the rib is a plate-like member having a constant plate thickness and extends in the radial direction from the outside surface of the bearing having a cylindrical shape.
  • a length (plate thickness) of the rib in the circumferential direction is constant. Accordingly, for example, when the bearing and the cylinder are integrally formed by injection molding and are removed in the predetermined direction from a mold, the rib and the mold do not interfere with each other, and thus the bearing and the cylinder can be easily removed from the mold.
  • a plurality of the ribs are provided, and the plurality of ribs are arranged side by side at predetermined intervals in the circumferential direction of the bearing.
  • the plurality of ribs are arranged side by side at predetermined intervals in the circumferential direction of the bearing.
  • rigidity in a plurality of inclination directions can be improved.
  • thermal expansion or shrinkage of the bearing is absorbed by the ribs.
  • inclination of the drive shaft due to thermal expansion or shrinkage of the bearing can be reduced.
  • the ribs function as inflow paths of the composite material. Accordingly, the composite material can easily and uniformly flow throughout the entire integrated body of the bearing and the cylinder.
  • each fiber contained in the composite material extends along an inflow direction. Since the inflow direction is substantially the same as the inclination direction of the drive shaft, rigidity with respect to the inclination direction of the drive shaft can be improved.
  • a rotary compressor according to an aspect of the present disclosure further includes a bearing wear-resistant portion (36) disposed between the bearing and the drive shaft and formed of a metal material, wherein the bearing is formed of the composite material, and the bearing wear-resistant portion is disposed at both end portions of the bearing in the predetermined direction.
  • the bearing wear-resistant portion is provided between the bearing and the drive shaft. This improves a limit PV value, and thus the wear of the bearing due to the rotation of the drive shaft can be reduced.
  • the bearing wear-resistant portion is disposed at both end portions of the bearing in the predetermined direction. That is, the bearing wear-resistant portion is not disposed at a central portion of the bearing.
  • the bearing is more likely to deform in response to the deformation of the drive shaft as compared to a case where the bearing wear-resistant portions are disposed over substantially the entire range of the bearing in the predetermined direction. That is, the bearing wear-resistant portions are unlikely to restrict the deformation of the bearing. Since the bearing deforms in response to the deformation of the drive shaft, even when the drive shaft deforms, a surface pressure acting on the bearing can be reduced, and thus the wear of the bearing can be reduced.
  • the volume of the bearing wear-resistant portions is reduced as compared to a case where the bearing wear-resistant portions are disposed over substantially the entire range of the bearing in the predetermined direction, and thus the manufacturing cost of the bearing wear-resistant portions can be reduced.
  • a rotary compressor further includes a blade that partitions the cylinder chamber into a suction side of the refrigerant and a discharge side of the refrigerant, in which the cylinder is formed of the composite material and includes a blade groove (44) configured to slidably accommodate the blade, and cylinder wear-resistant portions (45, 46) formed of a metal material are disposed at end portions of the blade groove on the cylinder chamber side.
  • the cylinder wear-resistant portions made of a metal material are disposed at the end portions of the blade groove on the cylinder chamber side.
  • wear of the cylinder due to the sliding of the blade can be reduced.
  • the cylinder wear-resistant portions are provided only at the end portions of the cylinder groove on the cylinder chamber side, the cylinder is more likely to deform in response to a load from the blade as compared to a case where the cylinder wear-resistant portions are disposed over substantially the entire range of the cylinder groove. That is, the cylinder wear-resistant portions are unlikely to restrict the deformation of the cylinder. Since the cylinder deforms responding to a load from the blade, a surface pressure acting on the cylinder can be reduced, and thus the wear of the cylinder can be reduced. Further, in this case, the volume of the cylinder wear-resistant portions is reduced as compared to a case where the cylinder wear-resistant portions are disposed over substantially the entire range of the blade groove, and thus the manufacturing cost of the cylinder wear-resistant portions can be reduced.
  • the cylinder is formed of the composite material, and the cylinder includes a suction port (43) that guides the refrigerant to the cylinder chamber and an excess thickness portion (66) disposed on an outer side of the suction port in the radial direction and protruding further outward in the radial direction than other regions.
  • the refrigerant at a low temperature before compression is guided to a suction port.
  • the temperature of a region near the suction portion becomes lower than the temperatures of other regions.
  • a region near the suction portion may deform due to a difference in temperature with other regions.
  • the refrigerant may leak from the cylinder chamber.
  • the cylinder includes the excess thickness portion disposed on the outer side of the suction portion in the radial direction.
  • a region near the suction portion can be made less likely to deform. Accordingly, even when the cylinder is formed of the composite material, deformation of the cylinder can be suppressed, and thus the leakage of the refrigerant from the cylinder chamber can be suppressed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP21903371.9A 2020-12-11 2021-12-06 Compresseur rotatif Pending EP4242462A4 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2020206161A JP2022093072A (ja) 2020-12-11 2020-12-11 ロータリ圧縮機
PCT/JP2021/044768 WO2022124271A1 (fr) 2020-12-11 2021-12-06 Compresseur rotatif

Publications (2)

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EP4242462A1 true EP4242462A1 (fr) 2023-09-13
EP4242462A4 EP4242462A4 (fr) 2024-05-01

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EP21903371.9A Pending EP4242462A4 (fr) 2020-12-11 2021-12-06 Compresseur rotatif

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EP (1) EP4242462A4 (fr)
JP (1) JP2022093072A (fr)
WO (1) WO2022124271A1 (fr)

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS584790U (ja) * 1981-07-01 1983-01-12 松下電器産業株式会社 回転式圧縮機
JPS58220991A (ja) * 1982-06-15 1983-12-22 Sanyo Electric Co Ltd 回転圧縮機
JPS6385269A (ja) * 1986-09-29 1988-04-15 Toshiba Corp コンプレツサ
JPH0768954B2 (ja) * 1987-04-02 1995-07-26 ダイキン工業株式会社 回転式圧縮機
JPH07217574A (ja) * 1994-02-03 1995-08-15 Daikin Ind Ltd 圧縮機
JP5833797B1 (ja) * 2014-06-12 2015-12-16 三桜工業株式会社 負圧ポンプ及びその製造方法
JP6548915B2 (ja) * 2015-03-05 2019-07-24 三菱重工サーマルシステムズ株式会社 圧縮機
JP7235577B2 (ja) * 2019-04-19 2023-03-08 三菱重工サーマルシステムズ株式会社 ロータリ圧縮機

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EP4242462A4 (fr) 2024-05-01
JP2022093072A (ja) 2022-06-23

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