EP4290078B1 - Rotationsverdichter - Google Patents

Rotationsverdichter

Info

Publication number
EP4290078B1
EP4290078B1 EP22749871.4A EP22749871A EP4290078B1 EP 4290078 B1 EP4290078 B1 EP 4290078B1 EP 22749871 A EP22749871 A EP 22749871A EP 4290078 B1 EP4290078 B1 EP 4290078B1
Authority
EP
European Patent Office
Prior art keywords
bearing
vane
cylinder
circumferential surface
roller
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.)
Active
Application number
EP22749871.4A
Other languages
English (en)
French (fr)
Other versions
EP4290078A4 (de
EP4290078A1 (de
Inventor
Bumdong SA
Seseok SEOL
Seoungmin Kang
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.)
LG Electronics Inc
Original Assignee
LG Electronics Inc
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 LG Electronics Inc filed Critical LG Electronics Inc
Publication of EP4290078A1 publication Critical patent/EP4290078A1/de
Publication of EP4290078A4 publication Critical patent/EP4290078A4/de
Application granted granted Critical
Publication of EP4290078B1 publication Critical patent/EP4290078B1/de
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/30—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C18/34—Rotary-piston pumps specially adapted for elastic fluids having the characteristics covered by two or more of groups F04C18/02, F04C18/08, F04C18/22, F04C18/24, F04C18/48, or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having the movement defined in group F04C18/08 or F04C18/22 and relative reciprocation between the co-operating members
    • F04C18/344—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 inner member
    • F04C18/3441—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 inner member the inner and outer member being in contact along one line or continuous surface substantially parallel to the axis of rotation
    • 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
    • F04C2/00—Rotary-piston machines or pumps
    • F04C2/30—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F04C2/34—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members
    • F04C2/344—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member
    • F04C2/3448—Rotary-piston machines or pumps having the characteristics covered by two or more groups F04C2/02, F04C2/08, F04C2/22, F04C2/24 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 groups F04C2/08 or F04C2/22 and relative reciprocation between the co-operating members with vanes reciprocating with respect to the inner member with axially movable vanes
    • 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
    • F04C18/344—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 inner member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—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
    • 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
    • F01C21/08—Rotary pistons
    • F01C21/0809—Construction of vanes or vane holders
    • F01C21/0818—Vane tracking; control therefor
    • F01C21/0827—Vane tracking; control therefor by mechanical means
    • F01C21/0836—Vane tracking; control therefor by mechanical means comprising guiding means, e.g. cams, rollers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F04C2210/261—Carbon dioxide (CO2)
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C2210/00—Fluid
    • F04C2210/26—Refrigerants with particular properties, e.g. HFC-134a
    • F04C2210/268—R32
    • 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
    • F04C2240/20—Rotors
    • 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
    • F04C2240/50—Bearings

Definitions

  • the present disclosure relates to a vane rotary compressor in which a vane is coupled to a rotating roller.
  • a rotary compressor may be divided into two types, namely, a type in which a vane is slidably inserted into a cylinder to be in contact with a roller, and another type in which a vane is slidably inserted into a roller to be in contact with a cylinder.
  • the former is called a roller eccentric rotary compressor (hereinafter, referred to as a "rotary compressor")
  • the latter is referred to as a vane concentric rotary compressor (hereinafter, referred to as a "vane rotary compressor”).
  • a vane inserted in a cylinder is pulled out toward a roller by elastic force or back pressure to come into contact with an outer circumferential surface of the roller.
  • a vane rotary compressor a vane inserted in a roller rotates together with the roller, and is pulled out by centrifugal force and back pressure to come into contact with an inner circumferential surface of a cylinder.
  • a rotary compressor independently forms compression chambers as many as the number of vanes per revolution of a roller, and the compression chambers simultaneously perform suction, compression, and discharge strokes.
  • a vane rotary compressor continuously forms as many compression chambers as the number of vanes per revolution of a roller, and the compression chambers sequentially perform suction, compression, and discharge strokes. Accordingly, the vane rotary compressor has a higher compression ratio than the rotary compressor. Therefore, the vane rotary compressor is more suitable for high pressure refrigerants such as R32, R410a, and CO2, which have low ozone depletion potential (ODP) and global warming index (GWP).
  • ODP ozone depletion potential
  • GWP global warming index
  • Patent Document 1 Such a vane rotary compressor is disclosed in Patent Document 1 (US Patent Publication No. US2015-0064042 A1 ).
  • the vane rotary compressor disclosed in Patent Document 1 has a structure in which suction refrigerant is filled in an inner space of a motor room as in a low-pressure type but a plurality of vanes are slidably inserted into a rotating roller.
  • an inner circumferential surface of a cylinder forming a compression space is defined by a plurality of curves.
  • the inner circumferential surface of the cylinder disclosed in Patent Document 1 may be formed in an asymmetrical elliptical shape that is eccentric with respect to an axial center of a rotating shaft. Accordingly, the inner circumferential surface of the cylinder is provided with a proximal portion closest to the axial center and a remote portion farthest from the axial center, and curved surfaces having different aspect ratios are connected between the proximal portion and the remote portion.
  • the roller is formed in a circular shape with a constant curvature on an outer circumferential surface and is disposed concentrically with respect to the axial center of the rotating shaft.
  • the roller is provided with a plurality of vane slots that are split and recessed by a predetermined depth at equal intervals along the outer circumferential surface.
  • an inner circumferential surface of the cylinder and an end portion of the vane i.e., sealing surface
  • Patent Document 2 Korean Patent Publication No. 10-2011-0095155 .
  • a structure for suppressing mechanical frictional loss between a vane and a cylinder by regulating a radial motion of the vane is known. That is, in Patent Document 2, a ring is disposed on a main bearing or a sub bearing, and a pin that slides along the ring in a circumferential direction is disposed on the vane. This merely allows the vane to perform a rotary motion along the roller and restricts a radial motion toward the cylinder. Then, since the vane always maintains its position relative to the cylinder, friction between the cylinder and the vane can be suppressed.
  • Patent Document 3 Japanese Laid-Open Patent Publication No. 2012-167578 .
  • a structure of restricting a contact between a front end portion (sealing surface) of a vane and a cylinder but enabling a radial motion of the vane is disclosed. That is, in Patent Document 3, a circular vane guide groove that is eccentric with respect to a bearing is provided, and a semicircular vane guide is applied to rotate along the vane guide groove. Accordingly, while moving radially with respect to an inner circumferential surface of the cylinder, the vane is maintained in a non-contact state with the inner circumferential surface of the cylinder. This may reduce mechanical frictional loss between the cylinder and the vane by reducing a contact area between the cylinder and the vane.
  • DE 492 322 C relates to a rotary piston machine that comprises a hardened race ring which creates the narrow gap between its piston drum and a housing cover that consists of one piece with the known race ring for the radial guidance of slide pistons, which has an angular cross-section. Further related technologies are disclosed in GB 280 253 A , JP S48 32202 A , US 3 988 083 A and JP S63 124885 A .
  • the present disclosure describes a rotary compressor capable of reducing mechanical frictional loss due to a rotation of a vane.
  • the present disclosure also describes a rotary compressor capable of reducing mechanical frictional loss between a main bearing or/and a sub bearing and a vane while restricting the vane from being drawn out by using the main bearing or/and sub bearing.
  • the present disclosure further describes a rotary compressor capable of reducing mechanical frictional loss between a main bearing or/and a sub bearing and a vane by providing a bearing member between the main bearing or/and sub bearing and the vane.
  • the present disclosure further describes a rotary compressor capable of reducing mechanical frictional loss due to a rotation of a roller.
  • the present disclosure further describes a rotary compressor capable of reducing mechanical frictional loss between a main bearing or/and a sub bearing and a roller facing the same.
  • the present disclosure further describes a rotary compressor capable of reducing mechanical frictional loss between a main bearing or/and sub bearing and a roller by providing a bearing member between the main bearing or/and sub bearing and the roller.
  • guide grooves are formed in a main bearing and a sub bearing supporting a rotating shaft, and guide protrusions are formed on a vane slidably inserted into a roller to be slidably inserted into the guide grooves and locked in a radial direction, and ball bearings may be disposed between the guide grooves and the guide protrusions.
  • This can facilitate a bearing member to be installed between the vane and the main bearing or sub bearing supporting the vane.
  • inner rings constituting the respective ball bearings may further include rotating plate portions extending between the main bearing and the roller and between the sub bearing and the roller. This can reduce mechanical frictional loss in an axial direction between the roller and the main bearing or sub bearing facing the roller.
  • the rotating plate portion is rotatably inserted into an inner circumferential surface of the cylinder. This can more effectively reduce the axial mechanical frictional loss between the roller and the main bearing or sub bearing facing the roller.
  • guide grooves are formed in a main bearing and a sub bearing supporting a rotating shaft, and guide protrusions are formed on a vane slidably inserted into a roller to be slidably inserted into the guide grooves and locked in a radial direction, a first bearing portion is disposed between the guide groove and the guide protrusion, a second bearing portion is disposed between the main bearing and the roller and/or between the sub bearing and the roller, and the first bearing portion and the second bearing portion may be formed integrally with each other. This can reduce radial frictional loss between the vane and the main or sub bearing and axial frictional loss between the roller and the main or sub bearing.
  • first bearing portion and the second bearing portion may be integrally formed with each other. This can facilitate manufacture of a bearing member that can reduce radial and axial frictional losses.
  • an outer circumferential surface of the second bearing portion may be disposed to face an inner circumferential surface of the cylinder, and a sealing portion may be formed on the outer circumferential surface of the second bearing portion. This can effectively suppress refrigerant leakage in a compression space even while the second bearing portion rotates in the cylinder.
  • an inner circumferential surface of the cylinder is formed in an annular shape.
  • the main bearing and the sub bearing disposed on both sides of the cylinder in an axial direction form a compression space together with the cylinder, and each has a guide groove on a side surface thereof forming the compression space.
  • a roller accommodated in the cylinder is disposed to rotate along with a rotating shaft.
  • At least one vane slidably inserted into the roller includes the guide protrusion that extends therefrom in the axial direction so as to be slidably inserted into the guide groove in a circumferential direction.
  • a bearing is disposed between the guide groove of at least one of the main bearing and the sub bearing and the guide protrusion of the vane. This configuration can reduce frictional loss between the vane and the main bearing or sub bearing supporting the vane, thereby enhancing compression efficiency.
  • the bearing includes: an outer ring inserted into an inner circumferential surface of the guide groove; an inner ring disposed inside the outer ring, and having an inner circumferential surface slidably brought into contact with a contact surface of the guide protrusion; and a sliding member disposed between the outer ring and the inner ring to allow a relative motion between the outer ring and the inner ring. This can more effectively reduce mechanical frictional loss between the vane and the main bearing or sub bearing and simultaneously facilitate installation of the bearing member.
  • One of the outer ring or the inner ring further includes a rotating plate portion extending between the roller and the main bearing and the sub bearing facing the roller. This can more effectively reduce axial mechanical frictional loss between the roller and the main bearing or sub bearing facing the roller.
  • the bearing includes: a first bearing portion disposed between at least one of the main bearing and the sub bearing and the vane facing the at least one bearing in a radial direction; and a second bearing portion disposed between at least one of the main bearing and the sub bearing and the roller facing the at least one bearing in an axial direction. This can reduce radial frictional loss between the vane and the main or sub bearing and axial frictional loss between the roller and the main or sub bearing.
  • first bearing portion and the second bearing portion may be integrally formed with each other. This can facilitate manufacture of the bearing member that can reduce the radial and axial frictional losses.
  • the second bearing portion may be thicker than the first bearing portion. Accordingly, a sealing area can be secured between the cylinder and the bearing member and simultaneously a sealing portion can be easily formed on an outer circumferential surface of the second bearing portion.
  • first bearing portion may be formed in an annular shape
  • second bearing portion may be formed in a disk shape
  • the first bearing portion may include: an outer ring inserted into the guide groove of at least one of the main bearing and the sub bearing; an inner ring disposed inside the outer ring, and having an inner circumferential surface slidably brought into contact with the guide protrusion of the vane; and a sliding member disposed between the outer ring and the inner ring to allow a relative motion between the outer ring and the inner ring.
  • the second bearing portion may extend radially from one end of the inner ring or the outer ring of the first bearing portion to be disposed on an axial side surface of the roller and an axial side surface of the at least one of the main bearing and the sub bearing facing the axial side surface of the roller. This can reduce radial frictional loss between the vane and the main or sub bearing and axial frictional loss between the roller and the main or sub bearing.
  • the second bearing portion may be disposed such that an axial side surface thereof is spaced apart from an axial side surface of the main bearing or the sub bearing facing the same. This can suppress a contact between the second bearing portion and the main bearing or the sub bearing, thereby effectively reducing frictional loss.
  • the second bearing portion may be inserted into the cylinder so that an outer circumferential surface thereof faces an inner circumferential surface of the cylinder. This can allow a sealing surface to be defined between the second bearing portion and the inner circumferential surface of the cylinder, thereby effectively reducing refrigerant leakage in the compression space.
  • a sealing portion may be disposed between the outer circumferential surface of the second bearing portion and the inner circumferential surface of the cylinder. This can more effectively suppress the refrigerant leakage in the compression space even while the second bearing portion is spaced apart from the cylinder.
  • the outer circumferential surface of the second bearing portion may have the same shape as the inner circumferential surface of the cylinder. This can allow the second bearing portion to rotate inside the cylinder, thereby suppressing a relative motion between the roller and the second bearing portion.
  • the bearing member may be disposed between at least one of the main bearing and the sub bearing and the vane facing the at least one bearing in a radial direction, and an axial side surface of the roller may be in sliding contact with an axial side surface of the main bearing and an axial side surface of the sub bearing facing the same. This can suppress mechanical frictional loss between the second bearing portion and the roller.
  • the inner circumferential surface of the cylinder may be formed in a circular or elliptical shape.
  • a discharge port may be formed in at least one of the axial side surface of the main bearing and the axial side surface of the sub bearing.
  • bush grooves may be formed in the roller, two swing bushes may be rotatably inserted into the bush grooves, and the vane may be slidably inserted between the swing bushes. This can allow a front end portion of the vane to have the same curvature as the inner circumferential surface of the cylinder, thereby securing a sealing area between the cylinder and the vane.
  • bearing members are disposed between guide grooves disposed in a main bearing and a sub bearing and guide protrusions of vanes facing the guide grooves. This configuration can reduce frictional loss between the vane and the main bearing or sub bearing supporting the vane, thereby enhancing compression efficiency.
  • a ball bearing that includes an outer ring, an inner ring, and a sliding member is disposed between an inner circumferential surface of the guide groove and the guide protrusion facing the guide groove. This can more effectively reduce the mechanical frictional loss between the vane and the main bearing or sub bearing and simultaneously facilitate installation of a bearing member.
  • one of the outer ring or the inner ring constituting the ball bearing further includes a rotating plate portion extending between the roller and the main bearing or the sub bearing facing the roller. This can more effectively reduce axial mechanical frictional loss between the roller and the main bearing or sub bearing facing the roller.
  • the rotary compressor according to the embodiment of the present disclosure may include a first bearing portion disposed between the main bearing and the sub bearing and the vane facing the same in a radial direction, and a second bearing portion disposed between the main bearing and the sub bearing and the roller facing the same in the axial direction. This can reduce radial frictional loss between the vane and the main or sub bearing and axial frictional loss between the roller and the main or sub bearing.
  • the first bearing portion and the second bearing portion may be formed integrally with each other. This can facilitate manufacture of a bearing member that can reduce radial and axial frictional losses.
  • the second bearing portion may be formed to be thicker than the first bearing portion. Accordingly, a sealing area can be secured between the cylinder and the bearing member and simultaneously a sealing portion can be easily formed on an outer circumferential surface of the second bearing portion.
  • the second bearing portion may be disposed such that an axial side surface thereof is spaced apart from an axial side surface of the main bearing or the sub bearing facing the same. This can suppress a contact between the second bearing portion and the main bearing or the sub bearing, thereby effectively reducing frictional loss.
  • the second bearing portion may be inserted into the cylinder so that its outer circumferential surface faces the inner circumferential surface of the cylinder. This can allow a sealing surface to be defined between the second bearing portion and the inner circumferential surface of the cylinder, thereby effectively reducing refrigerant leakage in the compression space.
  • a sealing portion may be disposed between the outer circumferential surface of the second bearing portion and the inner circumferential surface of the cylinder. This can more effectively suppress refrigerant leakage in the compression space even while the second bearing portion is spaced apart from the cylinder.
  • the inner circumferential surface of the cylinder may be formed in a circular or elliptical shape, and a discharge port may be formed through at least one of an axial side surface of the main bearing and an axial side surface of the sub bearing.
  • the inner circumferential surface of the cylinder can be formed in various shapes, and overcompression can be suppressed by extending a compression cycle.
  • bush grooves may be formed in the roller, two swing bushes may be rotatably inserted into the bush grooves, and the vane may be slidably inserted between the swing bushes. This can allow a front end portion of the vane to have the same curvature as the inner circumferential surface of the cylinder, thereby securing a sealing area between the cylinder and the vane.
  • a vane slot of a roller according to the present disclosure may be equally applied to a vane rotary compressor in which a vane is slidably inserted into the roller.
  • the present disclosure may be applied not only to an example in which the vane slot is formed in a radial direction but also to an example in which the vane slot is inclined.
  • FIG. 1 is a longitudinal sectional view of an exemplary vane rotary compressor according to the present disclosure
  • FIG. 2 is an exploded perspective view illustrating a compression unit in FIG. 1
  • FIG. 3 is an assembled perspective view of the compression unit in FIG. 2
  • FIG. 4 is a planar view of FIG. 3 .
  • a vane rotary compressor according to an embodiment of the present disclosure includes a casing 110, a driving (or drive) motor 120, and a compression unit 130.
  • the drive motor 120 is installed in an upper inner space 110a of the casing 110
  • the compression unit 130 is installed in a lower inner space 110a of the casing 110.
  • the drive motor 120 and the compression unit 130 are connected through a rotating shaft 123.
  • the casing 110 that defines an outer appearance of the compressor may be classified as a vertical type and a horizontal type according to a compressor installation method.
  • the vertical type casing the drive motor 120 and the compression unit 130 are disposed at upper and lower sides in an axial direction, respectively.
  • the horizontal type casing the drive motor 120 and the compression unit 130 are disposed at left and right sides, respectively.
  • the casing according to the embodiment of the present disclosure may be illustrated as the vertical type.
  • the casing 110 includes an intermediate shell 111 having a cylindrical shape, a lower shell 112 covering a lower end of the intermediate shell 111, and an upper shell 113 covering an upper end of the intermediate shell 111.
  • the drive motor 120 and the compression unit 130 may be inserted into the intermediate shell 111 to be fixed thereto, and a suction pipe 115 may penetrate through the intermediate shell 111 to be directly connected to the compression unit 130.
  • the lower shell 112 may be coupled to the lower end of the intermediate shell 111 in a sealing manner, and an oil storage space 110b in which oil to be supplied to the compression unit 130 is stored may be formed below the compression unit 130.
  • the upper shell 113 may be coupled to the upper end of the intermediate shell 111 in a sealing manner, and an oil separation space 110c may be formed above the drive motor 120 to separate oil from refrigerant discharged from the compression unit 130.
  • the drive motor 120 that constitutes a motor part supplies power to cause the compression unit 130 to be driven.
  • the drive motor 120 includes a stator 121, a rotor 122, and a rotating shaft 123.
  • the stator 121 may be fixedly inserted into the casing 110.
  • the stator 121 may be fixed to an inner circumferential surface of the cylindrical casing 110 in a shrink-fitting manner or the like.
  • the stator 121 may be press-fitted into an inner circumferential surface of the intermediate shell 111.
  • the rotor 122 may be rotatably inserted into the stator 121, and the rotating shaft 123 may be press-fitted into a center of the rotor 122. Accordingly, the rotating shaft 123 rotates concentrically together with the rotor 122.
  • An oil flow path 125 having a hollow hole shape may be formed in a central portion of the rotating shaft 123, and oil passage holes 126a and 126b may be formed through a middle portion of the oil flow path 125 toward an outer circumferential surface of the rotating shaft 123.
  • the oil passage holes 126a and 126b include a first oil passage hole 126a belonging to a range of a main bearing portion 1312 to be described later and a second oil passage hole 126b belonging to a range of a second bearing portion.
  • Each of the first oil passage hole 126a and the second oil passage hole 126b may be provided by one or in plurality. This embodiment shows an example in which a plurality of oil passage holes is formed.
  • An oil pickup 127 may be installed in a middle or lower end of the oil flow path 125.
  • a gear pump, a viscous pump, or a centrifugal pump may be used for the oil pickup 127.
  • This embodiment illustrates a case in which the centrifugal pump is employed. Accordingly, when the rotating shaft 123 rotates, oil filled in the oil storage space 110b is pumped by the oil pickup 127 and is sucked along the oil flow path 125, so as to be introduced into a sub bearing surface 1322b of the sub bush portion 1322 through the second oil passage hole 126b and into a main bearing surface 1311a of the main bearing portion 1312 through the first oil passage hole 126a. This will be described again later.
  • the compression unit 130 includes a main bearing 131, a sub bearing 132, a cylinder 133, a roller 134, and a plurality of vanes 1351,1352, and 1353.
  • the main bearing 131 and the sub bearing 132 are respectively provided at upper and lower parts of the cylinder 133 to define a compression space V together with the cylinder 133, the roller 134 is rotatably installed in the compression space V, and the vanes 1351, 1352, and 1353 are slidably inserted into the roller 134 to divide the compression space V into a plurality of compression chambers.
  • the main bearing 131 may be fixedly installed in the intermediate shell 111 of the casing 110.
  • the main bearing 131 may be inserted into the intermediate shell 111 and welded thereto.
  • the main bearing 131 may be coupled to an upper end of the cylinder 133 in a close contact manner. Accordingly, the main bearing 131 defines an upper surface of the compression space V, and supports an upper surface of the roller 134 in the axial direction while supporting an upper-half portion of the rotating shaft 123 in the radial direction.
  • the main bearing 131 may include a main plate portion 1311 and a main bearing portion 1312.
  • the main plate portion 1311 covers an upper part of the cylinder 133 to be coupled thereto, and the main bearing portion 1312 axially extends from a center of the main plate portion 1311 toward the drive motor 120 so as to support the upper portion of the rotating shaft 123.
  • the main plate portion 1311 may have a disk shape, and an outer circumferential surface of the main plate portion 1311 may be fixed to the inner circumferential surface of the intermediate shell 111 in a close contact manner.
  • a main guide groove 1311a may be formed in an axial lower surface of the main plate portion 1311, that is, in an axial lower surface that faces an upper surface of the roller 134 in the axial direction, to accommodate a guide protrusion 1351d to be described later.
  • the main guide groove 1311a may accommodate a main bearing hole 1312a to be described later, but may be formed eccentrically with respect to a bearing hole center (axial center or rotation center of the roller) (no reference numeral given) forming the center of the main bearing hole 1312a.
  • a center Og formed by an inner circumferential surface 1311a1 of the main guide groove 1311a may be aligned to be coaxial with a center Ov of the compression space V formed by an inner circumferential surface 1331 of the cylinder 133.
  • the center Og of the main guide groove 1311a and the center Ov of the compression space V may be formed eccentrically with respect to a rotation center Or of the roller 134.
  • the center Og of the main guide groove 1311a and the center Ov of the compression space V may be located on the same axis while being eccentric with respect to the rotation center Or of the roller 134.
  • the center Og of the main guide groove 1311a and the center Ov of the compression space V may be eccentric from each other.
  • the entirety of the main guide groove 1311a may be formed at approximately the same depth and communicate with the oil passage 125 provided in the rotating shaft 123.
  • the main guide groove 1311a may be formed in a stepped shape on an edge of an inner circumferential surface of the main plate portion 1311 or an edge of a lower end of the main bearing 131, the main guide groove 1311a may be located at a position where it communicates with the oil passage hole 126a of the rotating shaft 123 in the radial direction directly or through a main bearing surface 1312a1 that is formed by an inner circumferential surface of the main bearing hole 1312a. Accordingly, oil of discharge pressure or pressure equivalent thereto may be introduced into the main guide groove 1311a.
  • the inner circumferential surface of the main guide groove 1311a may be located at a position not communicating with the compression space V, for example, at a position between the main bearing surface 1312a1 formed by the inner circumferential surface of the main bearing hole 1312a and an outer circumferential surface 1341 of the roller 134. This can secure a sealing distance between the main bearing 131 and the roller 134. Accordingly, even if oil of discharge pressure or pressure equivalent thereto flows into the main guide groove 1311a, the oil may be suppressed from flowing into the compression space V.
  • the inner circumferential surface 1311a1 of the main guide groove 1311a may be formed in the same shape as an outer circumferential surface 1341 of the roller 134 to be described later.
  • the inner circumferential surface 1311a1 of the main guide groove 1311a may be formed in the same circular shape as the outer circumferential surface 1341 of the roller 134 to be described later. Accordingly, a sealing surface (or sealing distance) between the main guide groove 1311a and the outer circumferential surface of the roller can be defined uniformly along the circumferential direction.
  • the main bearing portion 1312 may be formed in the shape of a hollow bush through which the main bearing hole 1312a is formed, and an oil groove (not shown) may be formed in the main bearing surface 1312a1 that is the inner circumferential surface of the main bearing hole 1312a.
  • the sub bearing 132 may be coupled to be in close contact with the lower end of the cylinder 133. Accordingly, the sub bearing 132 defines a lower surface of the compression space V, and supports a lower surface of the roller 134 in the axial direction while supporting a lower-half portion of the rotating shaft 123 in the radial direction.
  • the sub bearing 132 may be formed similarly to the main bearing 131 described above.
  • the sub bearing 132 according to the embodiment of the present disclosure may include a sub plate portion 1321 and a sub bearing portion 1322.
  • the sub plate portion 1321 is coupled to the cylinder 133 to cover a lower side of the cylinder 133, and the sub bearing portion 1322 extends axially from a center of the sub plate portion 1321 toward the lower shell 112 to support the lower-half portion of the rotating shaft 123.
  • the sub plate portion 1321 may have a disk shape like the main plate portion 1311, and its outer diameter may be substantially the same as an outer diameter of the cylinder 133. Accordingly, an outer circumferential surface of the sub plate portion 1321 may be spaced apart from an inner circumferential surface of the intermediate shell 111.
  • a sub guide groove 1321a may be formed in an upper surface of the sub plate portion 1321 in the axial direction. Since the sub guide groove 1321a is formed symmetrically with the previously described main guide groove 1311a around the roller 134, the description of the sub guide groove 1321a will be replaced with the description of the main guide groove 1312a.
  • the sub bearing portion 1322 may be formed in the shape of a hollow bush through which the sub bearing hole 1322a is formed, and an oil groove (not shown) may be formed in the sub bearing surface 1322a1 that is an inner circumferential surface of the sub bearing hole 1322a.
  • the cylinder 133 may be in close contact with the lower surface of the main bearing 131 and may be coupled to the main bearing 131 by a bolt together with the sub bearing 132. Accordingly, the cylinder 133 may be fixedly coupled to the casing 110 by the main bearing 131.
  • the cylinder 133 may be formed in an annular shape having a compression space V in its center.
  • the inner circumferential surface 1331 of the cylinder 133 constituting the compression space V may be formed in a circular shape having the same inner diameter along the circumferential direction, and the center Ov of the compression space V (illustrated in FIG. 4 ) may be eccentric with respect to the rotation center Or (illustrated in FIG. 4 ) of the roller 134 constituting the axial center Os (illustrated in FIG. 4 ).
  • the inner circumferential surface 1331 of the cylinder 133 may be eccentric with respect to the outer circumferential surface 1341 of the roller 134, and a proximity point (or contact point) where the inner circumferential surface 1331 of the cylinder 133 and the outer circumferential surface 1341 of the roller 134 are almost in contact with each other may be formed between the inner circumferential surface 1331 of the cylinder 133 and the outer circumferential surface 1341 of the roller 134.
  • the cylinder 133 may be provided with a suction port 1332 and discharge ports 1333a and 1333b in both sides in the circumferential direction, respectively, based on the proximity point P. Accordingly, the suction port 1332 and the discharge ports 1333a and 1333b may be separated from each other by the proximity point P.
  • the suction port 1332 may be directly connected to a suction pipe 115 penetrating through the casing 110.
  • the discharge ports 1333a and 1333b may communicate with an inner space of the casing 110n to be indirectly connected to a discharge pipe 116 coupled through the casing 110. Accordingly, refrigerant may be suctioned directly into the compression space V through the suction port 1332 while compressed refrigerant may be discharged into the inner space of the casing 110 through the discharge port 1333a, 1333b, and then discharged to the discharge pipe 116.
  • the inner space of the casing 110 may be maintained in a high-pressure state forming discharge pressure.
  • a suction valve may not be separately disposed in the suction port 1332, however, discharge valves 1335a and 1335b for opening and closing the discharge ports 1333a and 1333b may be disposed in the discharge ports 1333a and 1333b, respectively.
  • Each of the discharge valves 1335a and 1335b may be a reed-type valve having one end fixed and another end free.
  • various types of valves such as a piston valve, other than the reed-type valve, may be used as the discharge valve 1335a, 1335b as necessary.
  • valve accommodating grooves 1334a and 1334b may be formed in the outer circumferential surface of the cylinder 133 to mount the discharge valves 1335a and 1335b therein, respectively. This can minimize the length of the discharge port 1333a, 1333b, thereby decreasing a dead volume.
  • Each of the valve accommodating grooves 1334a and 1334b may be formed in a triangular shape so as to secure a flat valve seat surface as illustrated in FIG. 2 .
  • the discharge port 1333a, 1333b may be provided in plurality along a compression path (a compression proceeding direction).
  • a discharge port located at an upstream side of the compression path is referred to as a first discharge port 1333a
  • a discharge port located at a downstream side of the compression path is referred to as a second discharge port 1333b.
  • the discharge port may not be provided in plurality.
  • the discharge port may not be provided in plurality.
  • the inner circumferential surface of the cylinder 133 has a long compression cycle to appropriately reduce overcompression of refrigerant, only one discharge port may be provided.
  • the roller 134 described above may be rotatably disposed in the compression space V of the cylinder 133.
  • the roller 134 may be formed so that its rotation center Or is located on the same axis as the axial center Os of the rotating shaft 123.
  • the roller 134 may be integrally formed or assembled with the rotating shaft 123. Accordingly, the roller 134 can rotate together with the rotating shaft 123 centering on the axial center Os.
  • the outer circumferential surface 1341 of the roller 134 may be formed in a circular shape, and a plurality of bush grooves 1342 may be formed in the outer circumferential surface 1341 of the roller 134 at preset intervals along the circumferential direction.
  • the bush grooves 1342 may be defined as a first bush groove (no reference numeral given), a second bush groove (no reference numeral given), and a third bush groove (no reference numeral given) along the compression proceeding direction (rotating direction of the roller), and the first bush groove, the second bush groove, and the third bush groove may be formed identically.
  • a swing bush 1343 that forms a kind of vane slot may be rotatably coupled to each bush groove 1342.
  • the swing bush 1343 two bushes formed in a substantially semicircular shape may be inserted into the bush grooves 1342 at an interval equal to a thickness of the vane 1351, 1352, 1353. Accordingly, the vane 1351, 1352, 1353 coupled to the swing bush 1343 may rotate using the swing bush 1343 as a hinge point while moving along the inner circumferential surface 1331 of the cylinder 133.
  • the vane 1351, 1352, 1353 when the vane 1351, 1352, 1353 is rotatably supported relative to the roller 134 by the swing bush 1343, the vane 1351, 1352, 1353 may always face the center Ov of the compression space V even though the roller 134 rotates in the state where the rotation center Or of the roller 134 is eccentric from the center Ov of the compression space V. Then, a vane front end portion 1351b, 1352b, 1353b defining a front surface of the vane 1351, 1352, 1363, which will be described later, may be formed to have the same curvature as the inner circumferential surface 1331 of the cylinder 133, to secure a sealing area between the vane 1351, 1352, 1363 and the cylinder 133.
  • a back pressure chamber 1344 may be formed inside the bush groove 1342, that is, between the bush groove 1342 and the rotation center Or of the roller 134.
  • the back pressure chamber 1344 may communicate with the bush groove 1342 in the radial direction and at the same time communicate with the main guide groove 1311a or/and the sub guide groove 1321a described above in the axial direction.
  • the vane 1351, 1352, 1353 may be pressed toward the inner circumferential surface 1331 of the cylinder 133 by pressure of high-pressure oil (or refrigerant) that flows into the main guide groove 1311a or/and the sub guide groove 1321a.
  • Each of the back pressure chambers 1344 may be sealed by the main bearing 131 and the sub bearing 132, and as described above, may axially communicate with the main guide groove 1311a or/and the sub guide groove 1321a.
  • the back pressure chamber 1344 may communicate with the main guide groove 1311a or/and the sub guide groove 1321a.
  • each of the plurality of vanes 1351, 1352, and 1353 may include a vane body 1351a, 1352a, 1353a, a front end portion (or front surface) 1351b, 1352b, 1353b, a vane rear end portion (or rear surface) 1351c, 1352c, 1353c, and guide protrusions 1351d, 1352d, 1353d.
  • the vane front end portion 1351b, 1352b, 1353b may be understood as a surface in contact with the inner circumferential surface 1331 of the cylinder 133, and the vane rear end portion 1351c, 1352c, and 1353c may be understood as a surface facing the back pressure chamber 1343a, 13343b, 1343c.
  • Each of the vane bodies 1351a, 1352a, and 1353a may be formed in a substantially rectangular parallelepiped shape. Accordingly, each of the vane bodies 1351a, 1352a, and 1353a can smoothly slide between the swing bushes 1343 along the longitudinal direction.
  • Each of the vane front end portions 1351b, 1352b, and 1353b may be formed in a curved shape so as to be in line-contact with the inner circumferential surface 1331 of the cylinder 133, and a sealing surface defining the front surface of the vane front end portion 1351b, 1352b, 1353b may have substantially the same curvature as the inner circumferential surface 1331 of the cylinder 133. Accordingly, even if the vane front end portion 1351b, 1352b, 1353b is slightly spaced apart from the inner circumferential surface 1331 of the cylinder 133, a sealing area between the vane front end portion 1351b, 1352b, 1353b and the cylinder can be secured, thereby suppressing leakage between compression chambers.
  • the vane rear end portions 1351c, 1352c, and 1353c may be formed flat. Accordingly, a pressure receiving surface defining a rear surface of each vane rear end portion 1351c, 1352c, and 1353c may evenly receive back pressure force of the back pressure chamber 1344, and the vane 1351, 1352, 1353 can stably behave while rapidly moving toward the cylinder 133.
  • the guide protrusions 1351d, 1352d, and 1353d may extend axially from both rear axial side surfaces of the vane bodies 1351a, 1352a, and 1353a, respectively, constituting the vane rear end portions 1351c, 1352c, and 1353a.
  • the guide protrusions 1351d, 1352d, 1353d may include an upper guide protrusion (hereinafter, referred to as a first guide protrusion) 1351d1, (not shown), (not shown) extending axially upward toward the main guide groove 1311a, and a lower guide protrusion (hereinafter, referred to as a second guide protrusion) 1351d2, (not shown), (not shown) extending axially downward toward the sub guide groove 1321a.
  • a first guide protrusion hereinafter, referred to as a first guide protrusion
  • a second guide protrusion 1351d2 extending axially downward toward the sub guide groove 1321a
  • the first guide protrusion 1351d1, (not shown), (not shown) and the second guide protrusion 1351d2, (not shown), (not shown) may have the same shape and size and be formed on the same axis. However, in some cases, the first guide protrusion 1351d1, (not shown), (not shown) and the second guide protrusion 1351d2, (not shown), (not shown) may be formed in different shapes and sizes, and may be located at positions eccentric from each other.
  • a description will be mainly given of an example in which the first guide protrusion 1351d1, (not shown), (not shown) and the second guide protrusion 1351d2, (not shown), (not shown) have the same shape and size and are formed on the same axis.
  • the first guide protrusion 1351d1, (not shown), (not shown) and the second guide protrusion 1351d2, (not shown), (not shown) mat have the same width as the vane body 1351a, 1352a, 1353a.
  • the first guide protrusion 1351d1, (not shown), (not shown) and the second guide protrusion 1351d2, (not shown), (not shown) may be wider or narrower than the vane body 1351a, 1352ad, 1353a.
  • first guide protrusion 1351d1, (not shown), (not shown) and the second guide protrusion 1351d2, (not shown), (not shown) may extend in the circumferential direction from both side surfaces or one side surface of the vane body 1351a, 1352ad, 1353a.
  • first guide protrusion 1351d1, (not shown), (not shown) and the second guide protrusion 1351d2, (not shown), (not shown) may preferably formed in an arcuate shape to correspond to the inner circumferential surface 1311a1, 1321a1 of each guide groove 1311a, 1321a.
  • first guide protrusions 1351d1, 1352d1, and 1353d1 and the second guide protrusions 1351d2, 1352d2, and 1353d2 may be formed identically in the circumferential direction, but may be formed differently in the circumferential direction.
  • the first guide protrusion 1351d1, (not shown), (not shown) and the second guide protrusion 1351d2, (not shown), (not shown) may each have a flat outer circumferential surface.
  • outer circumferential surfaces of the first guide protrusion 1351d1, (not shown), (not shown) and the second guide protrusion 1351d2, (not shown), (not shown) may be preferably formed in a circular curved shape to correspond to the inner circumferential surfaces 1311a1 and 1321a1 of the respective guide grooves 1311a and 1321a, more precisely, an inner circumferential surface 1365a of the first bearing portion 1365 to be described later.
  • vane bearings 136 and 137 may be disposed between the outer circumferential surfaces of the first guide protrusions 1351d1, 1352d1, and 1353d1 and the second guide protrusions 1351d2, 1352d2, and 1353d2 and the inner circumferential surfaces 1311a1 and 1321a1 of the main guide groove 1311a and the sub guide groove 1321a facing them.
  • the vane bearings 136 and 137 may be configured as various bearings, such as ball bearings, roller bearings, bush bearings, foil bearings, etc. In the embodiment of the present disclosure, an example in which the vane bearings 136 and 137 are configured as the ball bearings will be described, and the description of the vane bearings 136 and 137 will be described again later.
  • the plurality of vanes 1351, 1352, and 1353 slidably inserted into the swing bushes 1343 of the roller 134 serving as vane slots are pulled out from or pushed into the roller 134 by centrifugal force generated by the rotation of the roller 134 and back pressure of the back pressure chambers 1343 disposed in the rear sides of the respective vanes 1351, 1352, and 1353, such that the vane front end portions 1351b, 1352b, and 1353b of the vanes 1351, 1352, and 1353 are brought into contact with the inner circumferential surface 1332 of the cylinder 133.
  • the compression space V of the cylinder 133 are partitioned by the plurality of vanes 1351, 1352, and 1353 into as many compression chambers (including suction chamber or discharge chamber) V1, V2, and V3 as the number of the vanes 1351, 1352, and 1353.
  • the compression chambers V1, V2, and V3 are changed in volume by the shape of the inner circumferential surface 1332 of the cylinder 133 and eccentricity of the roller 134 while moving in response to the rotation of the roller 134.
  • the plurality of vanes 1351, 1352, and 1353 are pulled out from the roller 134, and the vane front end portions 1351b, 1352b, and 1353b forming the front surfaces of the respective vanes 1351, 1352, and 1353 are brought into contact with the inner circumferential surface 1332 of the cylinder 133 to separate the compression chambers.
  • the vane 1351, 1352, 1353 may be pushed out from the cylinder 133 by receiving gas force of the compression chamber as pressure in the corresponding compression chamber increases. Then, a distance between the cylinder 133 and the vane 1351, 1352, 1353 may further increase so that refrigerant leakage may increase.
  • the back pressure applied to the vane rear end portions 1351c, 1352c, and 1353c may be appropriately lowered, so that the cylinder 133 and the vanes 1351, 1352, and 1353 can move relative to each other in a spaced state within a range that refrigerant does not leak between the inner circumferential surface 1331 of the cylinder 133 and the front surfaces of the vanes 1351, 1352, and 1353.
  • the main guide groove 1311a may be formed in the main plate portion 1311 and the sub guide groove 1321a may be formed in the sub plate portion 1321, respectively, and each vane body 1351a, 1352a, and 1353a facing the main guide groove 1311a and the sub guide groove 1321a may include the first guide protrusion 1351d1, (not shown), (not shown) on the axial upper end, and the second guide protrusion 1351d2, (not shown), (not shown) on the axial lower end.
  • first guide protrusion 1351d1, (not shown), (not shown) and the second guide protrusion 1351d2, (not shown), (not shown) may be caught by the main guide groove 1311a and the sub guide groove 1321a, thereby restricting the extent that the vane protrudes.
  • This can reduce the mechanical frictional loss between the cylinder 133 and the vanes 1351, 1352, and 1353 and suppress the refrigerant leakage by securing the back pressure acting on the vanes 1351, 1352, and 1353.
  • the vane bearings 136 and 137 described above may be disposed between the guide grooves 1311a and 1321a and the guide protrusions 1351d, 1352d and 1353d, respectively, to reduce the frictional loss between the guide grooves 1311a and 1321a and the guide protrusions 1351d, 1352d, and 1353d.
  • FIG. 5 is an enlarged sectional view of the compression unit in FIG. 1
  • FIG. 6 is a cut-out perspective view of the vane bearing in FIG. 5
  • FIG. 7 is a cross-sectional view illustrating a state in which the vane bearing of FIG. 6 is mounted on the main bearing.
  • the vane bearings 136 and 137 may be disposed between the main guide groove 1311a and the first guide protrusion 1351d1, (not shown), (not shown) and/or between the sub guide groove 1321a and the second guide protrusion 1351d2, (not shown), (not shown).
  • vane bearings 136 and 137 various types of bearings, such as ball bearings, roller bearings, bush bearings, foil bearings, etc. may be applied to the vane bearings 136 and 137, but in the embodiment of the present disclosure, an example in which the vane bearings 136 and 137 are made of ball bearings will be mainly described.
  • the vane bearings 136 and 137 may extend between the roller 134 and the main bearing 131 and the sub bearing 132 facing the roller 134.
  • the vane bearings 136 and 137 are disposed between the guide grooves 1311a and 1321a and the guide protrusions 1351d, 1352d and 1353d and between the roller 134 and the bearings 131 and 132, respectively.
  • the vane bearings 136 and 137 may be defined as a main-side vane bearing 136 that is disposed between the main guide groove 1311a and the first guide protrusion 1351d1, (not shown), (not shown), and a sub-side vane bearing 137 that is disposed between the sub guide groove 1321a and the second guide protrusion 1351d2, (not shown), (not shown), and hereinafter, the main-side vane bearing will be described as a representative example.
  • the vane bearing 136 may include an outer ring 1361, an inner ring 1362, and a plurality of balls 1363.
  • the outer ring 1361 may be formed in an annular shape, and a center Oob of the outer ring 1361 may be located on the same axis as the center Og of the main guide groove 1311a. In other words, the center Oob of the outer ring 1361 may be provided eccentrically with respect to the rotation center Or of the roller 134.
  • an outer diameter of the outer ring 1361 may be formed to be substantially the same as or slightly smaller than an inner diameter of the main guide groove 1311a.
  • the outer ring 1361 may be press-fitted into the main guide groove 1311a, and when the outer diameter of the outer ring 1361 is slightly smaller than the inner diameter of the main guide groove 1311a, the outer ring 1361 may freely rotate in the main guide groove 1311a.
  • the inner ring 1362 may include a first bearing portion 1365 and a second bearing portion 1366.
  • the first bearing portion 1365 may be formed in an annular shape
  • the second bearing portion 1366 may be formed in a disk shape with a hollow central portion.
  • An outer diameter of the first bearing portion 1365 may be smaller than that of the outer ring 1361 and an inner diameter thereof may be larger than that of the main bearing hole 1312a.
  • a center Ob1 of the first bearing portion 1365 may be located on the same axis as the center Oob of the outer ring 1361, that is, the center Ob1 of the first bearing portion 1365 may be eccentric with respect to the rotation center Or of the roller 134. Accordingly, the inner ring 1362 including the first bearing portion 1365 may be rotatably inserted inside the outer ring 1361.
  • the second bearing portion 1366 may extend in a flange shape from a lower end of the first bearing portion 1365 or an outer circumferential surface around the lower end.
  • the second bearing portion 1366 may extend integrally from the first bearing portion 1365 or may be formed separately to be assembled to the first bearing portion 1365 later.
  • a thickness t2 of the second bearing portion 1366 may be formed thicker than a thickness t1 of the first bearing portion 1365 to facilitate the formation of a sealing portion 1367, 1377 to be described later.
  • the thickness t2 of the second bearing portion 1366 may be thicker than the thickness t1 of the first bearing portion 1365, and even when a separate sealing portion 1367 is not formed, the thickness t2 of the second bearing portion 1366 may be thicker than the thickness t1 of the first bearing portion 1365.
  • a sealing area can be secured between an outer circumferential surface 1366a of the second bearing portion 1366 and the inner circumferential surface 1331 of the cylinder 133.
  • An inner diameter D1 of the second bearing portion 1366 may be large enough for the back pressure chamber 1344 to communicate with the main guide groove 1311a, for example, may be smaller than an inner diameter D2 of the main guide groove 1311a and larger than a diameter D3 of a virtual circle drawn by connecting inner ends of the respective back pressure chambers 1344. Accordingly, high-pressure oil flowing into the main guide groove 1311a can smoothly flow into each back pressure chamber 1344 without being blocked by the second bearing portion 1366.
  • An outer diameter D12 of the second bearing portion 1366 may be substantially equal to or slightly smaller than an inner diameter D4 of the inner circumferential surface 1331 of the cylinder 133, that is, the compression space V. Accordingly, the second bearing portion 1366 is, according to the claimed invention, rotatably inserted into the inner space of the cylinder 133, that is, the compression space V, so as to rotate together with the first bearing portion 1365 centering on the rotation center Or of the roller 134. Therefore, the first bearing portion 1365 may be defined as a rotating ring portion, and the second bearing portion 1366 may be defined as a rotating plate portion.
  • the second bearing portion 1366 may be formed such that one side surface thereof in the axial direction is spaced apart a preset gap t3 from a lower surface of the main plate portion 1311 or an upper surface of the sub plate portion 1321 facing the one side surface.
  • a lower end of the second bearing portion 1366 may be slightly longer than a lower end of the first bearing portion 1365, so that the second bearing portion 1366 is axially spaced apart from the main plate portion 1311 or the sub plate portion 1321. This can suppress the second bearing portion from being in contact with the main plate portion 1311 or the sub plate portion 1321 during the rotation of the second bearing portion, thereby reducing mechanical frictional loss.
  • the second bearing portions 1366 and 1375 of the vane bearings 136 and 137 disposed on both axial sides of the roller may seal both axial sides of the compression space V defining the inner space of the cylinder 133, thereby providing a substantial compression space.
  • a sealing portion 1367 for sealing the compression space V is further disposed between the outer circumferential surface of the second bearing portion 1366 and the inner circumferential surface 1331 of the cylinder 133 facing the same.
  • the sealing portion 1367 may include at least one or more sealing grooves provided in an annular shape on the outer circumferential surface of the second bearing portion 1366 along the circumferential direction.
  • FIGS. 8 and 9 are cross-sectional views illustrating different embodiments of a sealing portion of the vane bearing in FIG. 5 .
  • the sealing portion 1367 may be configured as a single sealing groove as shown in FIG. 5 or may be configured by a plurality of sealing grooves spaced apart from one another by preset intervals along the axial direction as shown in FIG. 8 . Accordingly, oil or refrigerant may be filled in the sealing portion 1367 to seal between compression chambers.
  • the sealing portion 1367 may be configured by including a sealing groove 1367a formed in the outer circumferential surface of the second bearing portion 1366, and a sealing member 1367b formed in an annular shape and inserted into the sealing groove 1367a.
  • the sealing member 1367b may be made of a Teflon material or the like having a lubricating property.
  • a plurality of balls 1363 may be inserted between the inner circumferential surface of the outer ring 1361 and the outer circumferential surface of the inner ring 1362. Accordingly, the inner ring 1362 in contact the first guide protrusion 1351d1, (not shown), (not shown) of the vane 1351, 1352, 1353 may perform a relative motion with respect to the outer ring 1361.
  • the aforementioned sub-side vane bearing 137 may be equally applied to a position between the sub guide groove 1321a of the sub bearing 132 and the second guide protrusion 1351d2, (not shown), (not shown) of the vane 1351, 1352, 1353.
  • the sub-side vane bearing 137 similar to the main-side vane bearing, includes an outer ring 1371, an inner ring 1372, and a plurality of balls 1373, and thus will be understood by the description of the main-side vane bearing 136.
  • the sub-side vane bearing 137 may alternatively be formed in a shape different from that of the main-side vane bearing 136.
  • the main-side vane bearing 136 may be configured as a ball bearing
  • the sub side vane bearing 137 may be configured as a roller bearing or bush bearing.
  • the vane bearings 136 and 137 configured as the ball bearings are disposed between the main guide groove 1311a and the first guide protrusion 1351d1, (not shown), (not shown) and between the sub guide groove 1321a and the second guide protrusion 1351d2, (not shown), (not shown).
  • the inner rings 1362 and 1372 may include the first bearing portions 1365 and 1375 between the guide protrusions 1351d, 1352d, and 1353d and the guide grooves 1311a and 1321a, and the second bearing portions 1366 and 1376 extending between the main plate portion 1311 and the upper surface of the roller 134 and between the sub plate portion 1321 and the lower surface of the roller 134, and the second bearing portions 1366 and 1376 may rotate together with the roller 134. This can significantly reduce even axial frictional loss that occurs between the main bearing 131 and the roller 134 and between the sub bearing 132 and the roller 134.
  • the frictional loss between the vane front end portion and the cylinder can be suppressed by limiting the extent that the vane protrudes and simultaneously radial frictional loss between the guide protrusion and the guide groove and axial frictional loss between the main bearing and the roller and between the sub bearing and the roller can be significantly reduced. This can reduce mechanical frictional loss in the compression unit, thereby enhancing efficiency of the compressor.
  • the previous embodiment illustrates that the inner ring includes the first bearing portion and the second bearing portion, but in some cases, the outer ring of the vane bearing may include the first bearing portion and the second bearing portion.
  • the main-side vane bearing will be mainly described, and a description of the sub-side vane bearing will be replaced with the description of the main-side vane bearing.
  • FIG. 10 is a cross-sectional view illustrating still another example of a vane bearing.
  • a main-side vane bearing 136 may include an outer ring 1361, an inner ring 1362, and a plurality of balls 1363. Since the outer ring 1361, the inner ring 1362, and the plurality of balls 1363 are similar to those of the previous embodiments, a detailed description thereof will be replaced by the description of the previous embodiments.
  • the outer ring 1361 may include a first bearing portion 1365 and a second bearing portion 1366, and the inner ring 1362 may be formed in an annular shape. Even in this case, the second bearing portion 1366 may be inserted into the compression space V of the cylinder 133 to define an upper surface of the compression space V.
  • An outer circumferential surface 1365a of the first bearing portion 1365 of the outer ring 1361 according to the embodiment may be fixed by being press-fitted to the inner circumferential surface 1311a1 of the main guide groove 1311a as in the previous embodiment, or may be inserted to be rotatable with respect to the inner circumferential surface 1311a1 of the main guide groove 1311a.
  • the second bearing portion 1366 may also be fixed to the main plate portion 1311. Accordingly, the outer circumferential surface 1366a of the second bearing portion 1366 and the inner circumferential surface 1331 of the cylinder 133 can be brought into close contact with each other, thereby suppressing leakage in the compression space V more effectively.
  • the inner circumferential surface of the cylinder 133 may be formed in various shapes, such as a symmetrical ellipse or an asymmetrical ellipse in which a plurality of ellipses are combined, in addition to a circular shape, thereby enhancing compression efficiency.
  • the second bearing portion 1366 may rotate together with the roller 134. Then, radial frictional loss in the first bearing portion 1365 as well as axial frictional loss in the second bearing portion 1366 can be suppressed, and thus compressor efficiency can be improved.
  • the previous embodiments illustrate that the inner ring or the outer ring of the vane bearing includes the first bearing portion and the second bearing portion, but in some cases, the inner ring or outer ring of the vane bearing may merely include the first bearing portion.
  • the main-side vane bearing will be mainly described, and a description of the sub-side vane bearing will be replaced with the description of the main-side vane bearing.
  • FIG. 11 is a cross-sectional view illustrating still another embodiment of a vane bearing.
  • a vane bearing 136 may include an outer ring 1361, an inner ring 1362, and a plurality of balls 1363. Since the outer ring 1361, the inner ring 1362, and the plurality of balls 1363 are similar to those of the previous embodiments, a detailed description thereof will be replaced by the description of the previous embodiments.
  • each of the outer ring 1361 and the inner ring 1362 may merely include a first bearing portion 1365.
  • the inner ring 1362 may merely include the first bearing portion 1365 disposed between the inner circumferential surface 1311a1 of the main guide groove 1311a and the first guide protrusion 1351d1, (not shown), (not shown).
  • the shape and size of the first bearing portion 1365 may be identical to those of the first bearing portion 1365 in the previous embodiments.
  • each of the outer ring 1361 and the inner ring 1362 merely includes the first bearing portions 1365, radial frictional loss that occurs between the inner circumferential surface 1311a1 of the main guide groove 1311a and the first guide protrusion 1351d1, (not shown), (not shown) can be suppressed.
  • the inner circumferential surface 1331 of the cylinder 133 may be formed in various shapes.
  • the inner circumferential surface 1331 of the cylinder 133 may be formed in a symmetrical ellipse or an asymmetrical ellipse in which a plurality of ellipses are combined, in addition to a circular shape.
  • the inner circumferential surface 1331 of the cylinder 133 can be formed so that a compression cycle in the compression space V becomes longer, which can reduce compression loss due to overcompression.
  • a discharge port (not shown) may be formed in the main plate portion 1311 or the sub plate portion 1321. This can suppress insufficient surface pressure with respect to the vane front end portion 1351b, 1352b, which may occur when the discharge port (not shown) is formed through the inner circumferential surface 1331 of the cylinder 133. Therefore, partial damage to the vane front end portion 1351b, 1352b, 1353b or the inner circumferential surface 1331 of the cylinder 133 facing the same can be suppressed, which may result in suppressing leakage between compression chambers and reduction in compression efficiency in advance.
  • the foregoing embodiments illustrate the examples in which the swing bushes are disposed in the roller, but the swing bush does not necessarily need to be provided.
  • the present disclosure may equally be applied even to a case where one or more vane slots are formed in an outer circumferential surface of a roller and a vane is slid into the vane slot, which is the configuration of a typical vane rotary compressor.

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

Claims (13)

  1. Rotationsverdichter, der aufweist:
    einen Zylinder (133), der eine Innenumfangsfläche in einer ringförmigen Form aufweist; ein Hauptlager (131) und ein Nebenlager (132), die auf beiden Seiten des Zylinders (133) in axialer Richtung angeordnet sind, um zusammen mit dem Zylinder (133) einen Verdichtungsraum zu bilden, wobei jedes eine Führungsnut (1311a, 1321a) an einer Seitenfläche davon aufweist, die den Verdichtungsraum bildet;
    eine Rolle (134), die in dem Zylinder (133) aufgenommen ist und sich zusammen mit einer Drehwelle (123) dreht;
    mindestens einen Flügel (1351, 1352, 1353), der verschiebbar in die Rolle (134) eingesetzt ist und mindestens einen Führungsvorsprung (1351d, 1352d, 1353d) aufweist, der sich in axialer Richtung erstreckt, so dass er verschiebbar in die Führungsnut (1311a, 1321a) von mindestens einem des Hauptlagers (131) oder des Nebenlagers (132) in Umfangsrichtung eingesetzt ist; und
    ein Lager (136, 137), das zwischen der Führungsnut (1311a, 1321a) von dem mindestens einen des Hauptlagers (131) und des Nebenlagers (132) und dem mindestens einen Führungsvorsprung (1351d, 1352d, 1353d) des Flügels (1351, 1352, 1353) angeordnet ist,
    wobei das Lager (136, 137) aufweist:
    einen Außenring (1361), der drehbar in eine Innenumfangsfläche der Führungsnut (1311a, 1321a) eingesetzt ist;
    einen Innenring (1362), der drehbar innerhalb des Außenrings (1361) angeordnet ist und eine Innenumfangsfläche aufweist, die gleitend mit einer Kontaktfläche des mindestens einen Führungsvorsprungs (1351d, 1352d, 1353d) in Kontakt gebracht ist; und
    ein Gleitelement, das zwischen dem Außenring (1361) und dem Innenring (1362) angeordnet ist, um eine Relativbewegung zwischen dem Außenring (1361) und dem Innenring (162) zu ermöglichen,
    dadurch gekennzeichnet, dass
    einer des Außenrings (1361) oder des Innenrings (1362) ferner einen Drehplattenabschnitt (1366) aufweist, der drehbar in einen Innenraum des Zylinders (133) eingesetzt ist und sich zwischen der Rolle (134) und dem Hauptlager (131) oder zwischen der Rolle (134) und dem der Rolle (134) zugewandten Nebenlager (132) erstreckt.
  2. Rotationsverdichter nach Anspruch 1, wobei ein Dichtungsabschnitt (1367) zwischen der Außenumfangsfläche des rotierenden Plattenabschnitts (1366) und der ihm gegenüberliegenden Innenumfangsfläche (1331) des Zylinders (133) angeordnet ist.
  3. Rotationsverdichter, der aufweist:
    einen Zylinder (133), der eine Innenumfangsfläche in einer ringförmigen Form aufweist;
    ein Hauptlager (131) und ein Nebenlager (132), die auf beiden Seiten des Zylinders (133) in axialer Richtung angeordnet sind, um zusammen mit dem Zylinder (133) einen Verdichtungsraum zu bilden, wobei jedes Lager eine Führungsnut (1311a, 1321a) an einer Seitenfläche aufweist, die den Verdichtungsraum bildet;
    eine Rolle (134), die in dem Zylinder (133) aufgenommen ist und sich zusammen mit einer Drehwelle (123) dreht;
    mindestens einen Flügel (1351, 1352, 1353), der verschiebbar in die Rolle (134) eingesetzt ist und mindestens einen Führungsvorsprung (1351d, 1352d, 1353d) aufweist, der sich in axialer Richtung erstreckt, so dass er verschiebbar in die Führungsnut (1311a, 1321a) von mindestens einem des Hauptlagers (131) oder des Nebenlagers (132) in Umfangsrichtung eingesetzt ist; und
    ein Lager (136, 137), das zwischen der Führungsnut (1311a, 1321a) von dem mindestens einen des Hauptlagers (131) und des Nebenlagers (132) und dem mindestens einen Führungsvorsprung (1351d, 1352d, 1353d) des Flügels (1351, 1352, 1353) angeordnet ist,
    dadurch gekennzeichnet, dass
    das Lager (136, 137) aufweist:
    einen ersten Lagerabschnitt (1365), der drehbar zwischen dem mindestens einen des Hauptlagers (131) und des Nebenlagers (132) und dem Flügel (1351, 1352, 1353) angeordnet ist, der dem mindestens einen des Hauptlagers (131) oder des Nebenlagers (132) in radialer Richtung zugewandt ist; und
    einen zweiten Lagerabschnitt (1366), der drehbar zwischen dem mindestens einen des Hauptlagers (131) und des Nebenlagers (132) und der Rolle (134) angeordnet ist, die dem mindestens einen des Hauptlagers (131) oder des Nebenlagers (132) in axialer Richtung zugewandt ist,
    wobei der zweite Lagerabschnitt (1366) auf beiden axialen Seiten der Rolle (134) angeordnet ist, um beide axialen Seiten des Verdichtungsraums (V) abzudichten.
  4. Rotationsverdichter nach Anspruch 3, wobei ein Dichtungsabschnitt (1367) zwischen der Außenumfangsfläche des zweiten Lagerabschnitts (1366) und der Innenumfangsfläche (1331) des Zylinders (133) angeordnet ist, die diesem zugewandt ist.
  5. Rotationsverdichter nach Anspruch 3 oder 4, wobei der erste Lagerabschnitt (1365) und der zweite Lagerabschnitt (1366) integral miteinander ausgebildet sind.
  6. Rotationsverdichter nach Anspruch 3 oder 4, wobei der zweite Lagerabschnitt (1366) dicker ist als der erste Lagerabschnitt (1365).
  7. Rotationsverdichter nach Anspruch 3 oder 4, wobei der erste Lagerabschnitt (1365) in einer Ringform ausgebildet ist und der zweite Lagerabschnitt (1366) in einer Scheibenform ausgebildet ist.
  8. Rotationsverdichter nach Anspruch 3 oder 4, wobei der erste Lagerabschnitt (1365) aufweist:
    einen Außenring (1361), der in die Führungsnut (1311a, 1321a) des mindestens einen des Hauptlagers (131) und des Nebenlagers (132) eingesetzt ist;
    einen Innenring, der innerhalb des Außenrings (1361) angeordnet ist und eine Innenumfangsfläche aufweist, die gleitend mit dem mindestens einen Führungsvorsprung (1351d, 1352d, 1353d) des Flügels (1351, 1352, 1353) in Kontakt gebracht ist; und
    ein Gleitelement, das zwischen dem Außenring (1361) und dem Innenring (1362) angeordnet ist, um eine Relativbewegung zwischen dem Außenring (1361) und dem Innenring (1362) zu ermöglichen,
    wobei sich der zweite Lagerabschnitt (1366) radial von einem Ende des Innenrings (1362) oder des Außenrings (1361) des ersten Lagerabschnitts (1365) erstreckt, so dass er an einer axialen Seitenfläche der Rolle (134) und einer axialen Seitenfläche des mindestens einen des Hauptlagers (131) und des Nebenlagers (132) angeordnet ist, die der axialen Seitenfläche der Rolle (134) zugewandt ist.
  9. Rotationsverdichter nach Anspruch 3 oder 4, wobei der zweite Lagerabschnitt (1366) so angeordnet ist, dass seine axiale Seitenfläche von der axialen Seitenfläche des mindestens einen des Hauptlagers (131) oder des Nebenlagers (132), die dieser zugewandt ist, beabstandet ist.
  10. Rotationsverdichter nach Anspruch 3 oder 4, wobei der zweite Lagerabschnitt (1366) so in den Zylinder (133) eingesetzt ist, dass seine Außenumfangsfläche einer Innenumfangsfläche des Zylinders (133) zugewandt ist.
  11. Rotationsverdichter nach Anspruch 10, wobei ein Dichtungsabschnitt zwischen der Außenumfangsfläche des zweiten Lagerabschnitts (1366) und der Innenumfangsfläche des Zylinders (133) angeordnet ist.
  12. Rotationsverdichter nach Anspruch 10, wobei die Außenumfangsfläche des zweiten Lagerabschnitts (1366) die gleiche Form wie die Innenumfangsfläche des Zylinders (133) aufweist.
  13. Rotationsverdichter nach einem der Ansprüche 1 bis 12, wobei in der Rolle (134) Buchsennuten (1342) ausgebildet sind, zwei Schwenkbuchsen (1343) drehbar in die Buchsennuten (1342) eingesetzt sind und die Flügel (1351, 1352, 1353) verschiebbar zwischen den Schwenkbuchsen (1343) eingesetzt ist.
EP22749871.4A 2021-02-04 2022-01-06 Rotationsverdichter Active EP4290078B1 (de)

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KR1020210016193A KR102499761B1 (ko) 2021-02-04 2021-02-04 로터리 압축기
PCT/KR2022/000227 WO2022169117A1 (ko) 2021-02-04 2022-01-06 로터리 압축기

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EP (1) EP4290078B1 (de)
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DE492322C (de) * 1930-02-21 Knorr Bremse Akt Ges Drehkolbenmaschine
GB280253A (en) * 1926-05-17 1927-11-17 William Reavell Improvements in rotary compressors, exhausters and engines
US3988083A (en) * 1971-08-28 1976-10-26 Daihatsu Kogyo Company Limited Non-contact vane pump
JPS4832202A (de) * 1971-08-28 1973-04-27
US4958995A (en) * 1986-07-22 1990-09-25 Eagle Industry Co., Ltd. Vane pump with annular recesses to control vane extension
JPS63124885A (ja) * 1986-11-14 1988-05-28 Eagle Ind Co Ltd ベ−ンポンプ
EP0767866A1 (de) * 1994-06-28 1997-04-16 EDWARDS, Thomas C. Flügelzellenmaschine
US6036462A (en) * 1997-07-02 2000-03-14 Mallen Research Ltd. Partnership Rotary-linear vane guidance in a rotary vane machine
FI122753B (fi) * 2008-04-17 2012-06-29 Greittek Oy Pyörivä polttomoottori ja hydraulimoottori
JP5366856B2 (ja) 2010-02-17 2013-12-11 三菱電機株式会社 ベーンロータリ型流体装置及び圧縮機
JP5660919B2 (ja) 2011-02-11 2015-01-28 三菱電機株式会社 ベーン型圧縮機
WO2013105463A1 (ja) * 2012-01-11 2013-07-18 三菱電機株式会社 ベーン型圧縮機
JP5826692B2 (ja) 2012-04-02 2015-12-02 カルソニックカンセイ株式会社 気体圧縮機
KR102591414B1 (ko) * 2017-02-07 2023-10-19 엘지전자 주식회사 밀폐형 압축기
CN110873048B (zh) * 2018-08-29 2023-01-20 朱秋萍 多类滑板平面旋转式压缩机

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CN116848322A (zh) 2023-10-03
KR102499761B1 (ko) 2023-02-15
WO2022169117A1 (ko) 2022-08-11
EP4290078A4 (de) 2024-11-13
EP4290078A1 (de) 2023-12-13
US20240369059A1 (en) 2024-11-07
KR20220112531A (ko) 2022-08-11

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