EP3315781B1 - Compresseur de type ouvert - Google Patents

Compresseur de type ouvert Download PDF

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Publication number
EP3315781B1
EP3315781B1 EP17198489.1A EP17198489A EP3315781B1 EP 3315781 B1 EP3315781 B1 EP 3315781B1 EP 17198489 A EP17198489 A EP 17198489A EP 3315781 B1 EP3315781 B1 EP 3315781B1
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EP
European Patent Office
Prior art keywords
connection surface
suction port
oil supply
refrigerant
axial direction
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
EP17198489.1A
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German (de)
English (en)
Other versions
EP3315781A1 (fr
Inventor
Hajime Sato
Yoshiaki Miyamoto
Hisao Mizuno
Akihiro Noguchi
Takashi Goto
Toshiyuki Shikanai
Shusaku Goto
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
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Publication date
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Publication of EP3315781A1 publication Critical patent/EP3315781A1/fr
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Publication of EP3315781B1 publication Critical patent/EP3315781B1/fr
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/0207—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form
    • F04C18/0215—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents both members having co-operating elements in spiral form where only one member is moving
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • F01C21/02—Arrangements of bearings
    • 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
    • F04C29/02—Lubrication; Lubricant separation
    • F04C29/028—Means for improving or restricting lubricant flow
    • 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
    • F01C21/007—General arrangements of parts; Frames and supporting elements
    • 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
    • F04C2240/56—Bearing bushings or details thereof

Definitions

  • the present invention relates to an open type compressor.
  • An open type compressor includes a drive shaft which is rotationally driven by an electric motor or an engine, a crank pin (eccentric shaft) which is provided at a position offset from the drive shaft, a turning scroll which is rotatably supported by the crank pin, and a fixed scroll which faces the turning scroll in a metal housing (for example, refer to Patent Document 1).
  • the turning scroll revolves (performs turning motion) about the axis of the drive shaft without rotating. Accordingly, a volume of a compression chamber formed between the fixed scroll and the turning scroll is changed, and a fluid introduced into the compression chamber is compressed.
  • a lip seal (oil seal having lip) is provided in a protrusion portion of the drive shaft, that is, a through-hole of the housing and prevents a refrigerant inside the housing from leaking to the outside.
  • the lip seal is lubricated by a mist-like lubricant introduced along with the refrigerant.
  • oil supplied to the lip seal is insufficient at a low load operation where a circulation amount of the refrigerant decreases, or the like.
  • Patent Document 1 discloses an open type compressor in which an oil supply path extending toward a lip seal and a bearing member positioned around the lip seal is formed on an inner wall surface of a housing and a refrigerant and a lubricant flowing through the inside of the housing during an operation are supplied to the lip seal and the bearing member via the oil supply path.
  • Patent Document 1 Japanese Unexamined Patent Application, First Publication No. 2016-156310
  • EP 0 133 625 discloses an open type scroll compressor comprising a compression mechanism, a drive shaft, a bearing, a housing and an oil supply path.
  • EP 2 708 750 and US 5 888 057 disclose other open type scroll compressors.
  • an object of the present invention is to provide an open type compressor capable of preventing a refrigerant including a lubricant from flowing without being introduced to the oil supply path.
  • an open type scroll compressor as defined by claim 1.
  • the refrigerant after the refrigerant introduced from the suction port hits with the first surface, the refrigerant flows to the connection surface to reach the second surface. Therefore, the refrigerant easily stagnates in the vicinity of the connection surface on which an oil supply port is formed, and it is possible to prevent the refrigerant from flowing without being introduced to the oil supply path.
  • the suction port may be formed in a tubular shape, and a portion of an opening portion of the suction port and a portion of the opening portion of the oil supply path may overlap each other when viewed in an extension direction of the suction port.
  • the refrigerant introduced from the suction port can be easily introduced to the oil supply path.
  • connection surface includes a first connection surface which is parallel to the axis and a second connection surface which is connected to one side of the first connection surface in the axial direction and faces the other side in the axial direction, and the opening portion of the oil supply path is formed on the second connection surface.
  • the refrigerant flowing along the first connection surface and the second surface hits with the second connection surface facing the other side in the axial direction. Therefore, more refrigerant can be introduced to the oil supply path.
  • the refrigerant introduced from the suction port hits with the first surface
  • the refrigerant flows to the connection surface to reach the second surface. Therefore, the refrigerant easily stagnates in the vicinity of the connection surface on which an oil supply port is formed, and it is possible to prevent the refrigerant from flowing without being introduced to the oil supply path.
  • the open type compressor 1 (open type scroll compressor) of the present embodiment includes a bottomed cylindrical housing 2, a front housing 3 (side wall) which closes an opening of the housing 2, a drive shaft 5 which is rotationally driven around an axis A, a scroll compression mechanism 6 which is driven by the drive shaft 5, a main bearing 7 (bearing) which rotatably supports the drive shaft 5, and a sub bearing 8 which is disposed on the front housing 3 side with respect to the main bearing 7.
  • the drive shaft 5, the scroll compression mechanism 6, the main bearing 7, and the sub bearing 8 are accommodated in the housing 2.
  • the housing 2 extends in an axial direction Da in the axis A.
  • the housing 2 is formed in a bottomed cylindrical shape in which one end portion 2a is open and the other end portion 2b is closed.
  • the housing 2 includes a suction port 21 through which a refrigerant (refrigerant gas) which is a fluid and a mist-like lubricant are introduced to the inside of the housing 2 from the outside and a discharge opening 22 through which the refrigerant compressed by the scroll compression mechanism 6 is discharged to the outside of the housing 2.
  • a refrigerant refrigerant gas
  • a direction in which the axis A extends is referred to as the axial direction Da.
  • a protrusion direction of the drive shaft 5 is referred to as one side Da1 (left side in FIG. 1 ) in the axial direction and a side opposite to the one side Da1 in the axial direction is referred to as the other side Da2 (right side in FIG. 1 ) in the axial direction.
  • a radial direction based on the axis A is simply referred to as a radial direction.
  • a direction around the axis about the axis A is referred to as a circumferential direction.
  • the front housing 3 is attached to the housing 2 to close an opening of the housing 2 on the one side Da1 (one end portion 2a side) in the axial direction.
  • the front housing 3 configures a side wall of the housing 2.
  • the front housing 3 is fixed to the housing 2, and thus, forms a sealed space inside the housing 2 along with the housing 2.
  • the scroll compression mechanism 6 and the drive shaft 5 are accommodated in the sealed space.
  • a through-hole 32 penetrating the front housing 3 in the axial direction Da is formed at the center portion of the front housing 3.
  • the drive shaft 5 is inserted into the through-hole 32.
  • a bearing holding portion 33 which extends in a tubular shape toward the other side Da2 in the axial direction is formed in a portion of the front housing 3 inserted into the housing 2.
  • the front housing 3 includes an annular front housing base portion 31 which is fitted to one end portion 2a of the housing 2 and the bearing holding portion 33 which protrudes from the front housing base portion 31 to the other side Da2 in the axial direction.
  • the bearing holding portion 33 is a portion which holds the main bearing 7 from the outside in the radial direction.
  • a first oil supply path 81 (oil supply path) is formed, which penetrates the bearing holding portion 33 from the outside of the bearing holding portion 33 in the radial direction to the inside of the bearing holding portion 33 in the radial direction.
  • An opening portion 81a on the outside of the first oil supply path 81 in the radial direction is open to an outer peripheral surface of the bearing holding portion 33.
  • An end portion on the inside of the first oil supply path 81 in the radial direction is open to a portion between the main bearing 7 and the sub bearing 8 on an inner peripheral surface of the bearing holding portion 33. That is, the first oil supply path 81 connects the outside of the bearing holding portion 33 in the radial direction and the one side Da1 of the main bearing 7 in the axial direction on the inside of the bearing holding portion 33 in the radial direction to each other.
  • an internal space S3 and a second oil supply path 82 which communicates with an outer peripheral side of the sub bearing 8 inside the through-hole 32 are formed.
  • An opening portion 21a of the suction port 21 is formed in a tubular shape.
  • a center axis As of the opening portion 21a of the suction port 21 extends in up and down directions Dv. Accordingly, the refrigerant introduced from the suction port 21 flows in the up and down directions Dv.
  • a plurality of first oil supply paths 81 and second oil supply paths 82 are formed at intervals therebetween in a circumferential direction Dc.
  • the four first oil supply paths 81 and the four second oil supply paths 82 are provided at intervals of 90° in the circumferential direction Dc.
  • the first oil supply paths 81 and the second oil supply paths 82 are formed such that a center axis of each of the first oil supply paths 81 and a center axis of each of the second oil supply paths 82 coincide with each other.
  • One of the four first oil supply paths 81 is provided immediately below the suction port 21. This first oil supply path 81 is referred to as a main oil supply path 81M.
  • the front housing 3 includes a plurality of ribs 34 which protrude from the front housing base portion 31 toward the other side Da2 in the axial direction and a compression mechanism support portion 35 which is provided on end portions on the other side Da2 of the plurality of ribs 34 in the axial direction.
  • a gap is formed between the ribs 34 and the inner peripheral surface of the housing 2.
  • the drive shaft 5 is rotationally driven around the axis A.
  • the drive shaft 5 extends in the axial direction Da.
  • the drive shaft 5 is rotatably supported by the front housing 3 via the main bearing 7 and the sub bearing 8.
  • One end portion 5a which is the one side Da1 of the drive shaft 5 in the axial direction protrudes from the front housing 3 to the outside in a state where the drive shaft 5 is inserted into the through-hole 32.
  • a lip seal 9 is provided between the drive shaft 5 and the through-hole 32 to secure sealability.
  • a disk-shaped disk portion 5d is formed on an end portion on the other side Da2 (the other end portion 2b side of the housing 2) of the drive shaft 5 in the axial direction.
  • a crank pin 51 is provided at a position eccentric by a predetermined dimension in the radial direction on the other side Da2 of the disk portion 5d of the drive shaft 5 in the axial direction.
  • the crank pin 51 protrudes from the end portion of the disk portion 5d of the drive shaft 5 toward the other side Da2 in the axial direction.
  • the crank pin 51 is integrally formed with the end portion on the other side Da2 of the drive shaft 5 in the axial direction. If the drive shaft 5 rotates in the circumferential direction Dc, the crank pin 51 turns along a circular orbit having an eccentric dimension in the radial direction with respect to the axis A as a radius.
  • the main bearing 7 is fixed to the inside of the bearing holding portion 33 of the front housing 3.
  • the disk portion 5d is fitted to the inside of the main bearing 7 and is rotatably supported by the main bearing 7.
  • the sub bearing 8 is disposed on the one side Da1 (the front housing 3 side) in the axial direction with respect to the main bearing 7.
  • the sub bearing 8 is provided inside the through-hole 32 of the front housing 3.
  • the drive shaft 5 is rotatably supported via the sub bearing 8 in an intermediate portion between the one end portion 5a and the disk portion 5d in the axial direction Da.
  • a pulley 11 is rotatably provided in the front housing 3 via a bearing 10.
  • a belt which transmits a driving force from a drive source such as a motor or an engine is wound around the pulley 11.
  • the pulley 11 and the one end portion 5a of the drive shaft 5 are connected to each other via an electromagnetic clutch 12. If power which drives the pulley 11 and is input from the outside is transmitted to the drive shaft 5 via the electromagnetic clutch 12, the drive shaft 5 rotates around the axis A.
  • the scroll compression mechanism 6 is a mechanism which is connected to the drive shaft 5 and compresses a refrigerant including a lubricant.
  • the scroll compression mechanism 6 includes a fixed scroll 61 and a turning scroll 62.
  • the fixed scroll 61 integrally includes a disk-shaped fixed end plate 61a and a spiral fixed lap 61b uprightly standing on the one side Da1 in the axial direction with respect to the fixed end plate 61a.
  • the fixed end plate 61a is fixed to the other end portion 2b of the housing 2 via a bolt 63.
  • a discharge port 64 through which the refrigerant compressed by the scroll compression mechanism 6 is discharged is formed at the center portion of the fixed end plate 61a.
  • the fixed lap 61b is formed such that the height in the axial direction Da decreases in stages from the outer peripheral side toward the inner peripheral side.
  • a fixed scroll groove bottom surface 61c which is a surface on the side where the fixed lap 61b is formed, is formed to increase in stages from the outer peripheral side toward the inner peripheral side to the side where the fixed lap 61b uprightly stands.
  • An O ring 69 is provided on the other side Da2 of the outer peripheral surface of the fixed end plate 61a in the axial direction. The O ring 69 is in close contact with the inner peripheral surface of the housing 2.
  • a space between the inner peripheral surface of the housing 2 and the outer peripheral side of the fixed end plate 61a is divided into a discharge chamber S2 on the other side in the axial direction Da with respect to the O ring 69 and a suction chamber S1 on the one side in the axial direction Da on which the front housing 3 is disposed with respect to the O ring 69.
  • the suction chamber S1 communicates with the suction port 21 formed in the housing 2. A low-pressure refrigerant circulating in a refrigeration cycle is sucked from the suction port 21, and the refrigerant is sucked into the compression chamber 65 via the suction chamber S1.
  • the turning scroll 62 integrally includes a disk-shaped turning end plate 62a and a spiral turning lap 62b uprightly standing on the other side Da2 in the axial direction with respect to the turning end plate 62a.
  • the turning lap 62b extends toward the other side Da2 in the axial direction with respect to the turning end plate 62a.
  • the turning lap 62b is formed such that the height in the axial direction Da decreases in stages from the outer peripheral side toward the inner peripheral side.
  • a turning scroll groove bottom surface 62c which is a surface on the side where the turning lap 62b is provided, is formed to increase in stages from the outer peripheral side toward the inner peripheral side to the side where the turning lap 62b uprightly stands.
  • a drive bearing accommodation portion 66 in which a drive bearing 67 is accommodated is formed on the one side Da1 of the turning end plate 62a in the axial direction.
  • the drive bearing accommodation portion 66 is formed in a cylindrical shape protruding toward the one side Da1 in the axial direction.
  • the drive bearing 67 is fitted to an outer peripheral surface of a drive bush 68 fitted to the outer peripheral surface of the crank pin 51. Accordingly, the turning scroll 62 smoothly revolves around the fixed scroll 61 along with the crank pin 51 which turns along a circular orbit as the drive shaft 5 rotates around the axis A.
  • a main balance weight 71 and a sub balance weight 72 which cancel out eccentric forces generated by turning of the crank pin 51 and the turning scroll 62 are provided in the drive shaft 5.
  • the main balance weight 71 is provided between the drive shaft 5 and the turning scroll 62 in order to eliminate unbalance generated by the turning scroll 62 which turns eccentrically with respect to the axis A.
  • the main balance weight 71 is disposed to be adjacent to the other side Da2 in the axial direction with respect to the disk portion 5d.
  • the sub balance weight 72 is provided between the disk portion 5d of the drive shaft 5 and the sub bearing 8 in order to eliminate unbalance generated by the turning scroll 62 which turns eccentrically with respect to the axis A.
  • the sub balance weight 72 is disposed to be adjacent to the one side Da1 in the axial direction with respect to the disk portion 5d.
  • the fixed lap 61b of the fixed scroll 61 and the turning lap 62b of the turning scroll 62 are provided to engage with each other.
  • a pair of compression chambers 65 which is divided by the fixed end plate 61a and the fixed lap 61b and the turning end plate 62a and turning lap 62b and is spirally continuous, is symmetrically formed with respect to a scroll center between the fixed scroll 61 and the turning scroll 62. Accordingly, when the compression chambers 65 move while reducing the volume from the outer peripheral side to the center side to compress the refrigerant, the refrigerant is compressed in both the circumferential direction Dc and the axial direction Da of the fixed lap 61b and the turning lap 62b. Therefore, the scroll compression mechanism 6 becomes a so-called three-dimensional compressible structure.
  • a first surface 41 which is a surface intersecting a flow direction of the refrigerant
  • a connection surface 43 which is connected to the first surface 41 and is oblique to the first surface 41 so as to extend away from the suction port 21 as going away from the first surface 41
  • a second surface 42 which is connected to the connection surface 43 and is oblique to the connection surface 43 so as to extend close to the suction port 21 as going away from the connection surface 43.
  • the first surface 41 and the second surface 42 are connected to each other via the connection surface 43.
  • the first surface 41, the connection surface 43, and the second surface 42 form a stepped shape.
  • the opening portion 81a of the first oil supply path 81 is provided on the connection surface 43.
  • the first surface is a surface parallel to a horizontal surface.
  • the first surface 41 and the second surface 42 are formed in parallel.
  • connection surface 43 is connected to one side of the first surface 41 in the circumferential direction Dc and the second surface 42 is connected to one side of the connection surface 43 in the circumferential direction Dc.
  • the second surface 42 is formed at a position further away from the suction port 21 than the first surface 41.
  • connection surface 43 and the first surface 41 An obtuse angle is formed between the connection surface 43 and the first surface 41. Specifically, the angle formed between the connection surface 43 and the first surface 41 is approximately 120°.
  • the first surface 41 is provided at a position at which the refrigerant introduced from the suction port 21 hits.
  • the first surface 41 is orthogonal to the flow direction of the refrigerant.
  • the first surface 41 may be inclined to a horizontal surface by approximately ⁇ 10°.
  • the connection surface 43 includes a first connection surface 44 which is parallel to the axis A and a second connection surface 45 which a surface which is connected to the one side Da1 of the first connection surface 44 in the axial direction and faces the other side Da2 in the axial direction.
  • the second connection surface 45 has a rectangular shape, a first side 45a of the second connection surface 45 is connected to a side on the one side Da1 of the second surface 42 in the axial direction, and a second side 45b of the second connection surface 45 is connected to a side on the one side Da1 of the first connection surface 44 in the axial direction.
  • the opening portion 81a of the outside of the main oil supply path 81M in the radial direction is formed on the second connection surface 45.
  • an inlet side of the main oil supply path 81M is open to the second connection surface 45.
  • the bearing holding portion 33 and the compression mechanism support portion 35 are separated from each other in the axial direction Da.
  • the refrigerant introduced from the suction port 21 flows into the inside in the radial direction from a refrigerant passage hole 14 which is formed by the adjacent ribs 34, the bearing holding portion 33, and the compression mechanism support portion 35.
  • the refrigerant passage hole 14 may be closed.
  • a portion of the opening portion 21a of the suction port 21 and a portion of the opening portion 81a of the main oil supply path 81M overlap each other. That is, when viewed from above, a portion of the opening portion 81a of the main oil supply path 81M can be viewed via the opening portion 21a of the suction port 21.
  • the scroll compression mechanism 6 is driven by the drive shaft 5 and sucks the refrigerant flowing into the housing 2 from the suction port 21 formed on the housing 2 from the outer peripheral side into the compression chamber 65.
  • the refrigerant sucked into the compression chamber 65 is compressed by moving the compression chamber 65 from the outer peripheral position to the center position while gradually reducing the volume.
  • the compressed refrigerant is fed from the discharge port 64 formed on the fixed end plate 61a of the fixed scroll 61 to the discharge chamber S2 formed in a gap between the fixed end plate 61a of the fixed scroll 61 and the other end portion 2b of the housing 2. Thereafter, the refrigerant is discharged from the discharge opening 22 to a refrigeration cycle side outside the housing 2.
  • the mist-like lubricant is introduced from the suction port 21 into the housing 2 along with the refrigerant.
  • a portion of the mist-like lubricant introduced from the suction port 21 into the housing 2 is introduced into the internal space S3 of the bearing holding portion 33 via the first oil supply path 81.
  • the lubricant is supplied to the main bearing 7 by a portion of the lubricant introduced into the internal space S3.
  • a refrigerant G introduced from the suction port 21 hits with the first surface 41.
  • the refrigerant G which hits with the first surface 41 flows to the connection surface 43 to reach the second surface 42.
  • the refrigerant G staying on the connection surface 43 or the second surface 42 is introduced to the opening portion 81a of the main oil supply path 81M.
  • the refrigerant easily stagnates in the vicinity of the connection surface 43 on which the opening portion 81a of the main oil supply path 81M is formed and it is possible to prevent the refrigerant from flowing without being introduced to the main oil supply path 81M.
  • connection surface 43 An obtuse angle is formed between the connection surface 43 and the first surface 41, and thus, when the refrigerant which hits with the first surface 41 flows to the connection surface 43 side, it is possible to prevent the refrigerant from being separated from the connection surface 43. Therefore, more refrigerant can be introduced to the second surface 42 or the main oil supply path 81M.
  • connection surface 43 includes the first connection surface 44 parallel to the axis A and the second connection surface 45 which faces the other side Da2 in the axial direction, and the opening portion 81a of the first oil supply path 81 is formed on the second connection surface 45. Accordingly, more refrigerant can be introduced to the main oil supply path 81M.
  • the second oil supply path 82 is provided on the extension line of the first oil supply path 81.
  • the second oil supply path 82 may be omitted.

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

Claims (2)

  1. Compresseur à spirales de type ouvert comprenant :
    un mécanisme de compression (6) qui comprime un réfrigérant comprenant un lubrifiant ;
    un arbre d'entraînement (5) qui tourne autour d'un axe (A) pour entraîner le mécanisme de compression (6) ;
    un palier (7) qui supporte en rotation l'arbre d'entraînement (5) ; et
    un carter (2) qui comprend une paroi latérale (3) dans laquelle est formé un trou débouchant (32) à travers lequel l'arbre d'entraînement (5) fait saillie vers un côté dans une direction axiale (Da1), une partie de support de palier (33) qui fait saillie selon une forme tubulaire de la paroi latérale (3) vers l'autre côté dans la direction axiale (Da2) pour maintenir le palier (7), un orifice d'aspiration (21) à travers lequel le réfrigérant est introduit dans un intérieur du carter (2), et un passage d'alimentation en huile (81M) à travers laquelle le lubrifiant est introduit depuis un extérieur de la partie de support de palier (33) dans une direction radiale vers un côté du palier (7) dans la direction axiale (Da),
    caractérisé en ce que la partie de support de palier (33) comprend une première surface (41) qui est une surface qui est prévue dans une position dans laquelle le réfrigérant introduit par l'orifice d'aspiration (21) se heurte et coupant une direction d'écoulement du réfrigérant, une surface de raccordement (43) qui est raccordée à un côté de la première surface (41) dans une direction circonférentielle (Dc) et est oblique par rapport à la première surface (41) de manière à s'éloigner de l'orifice d'aspiration (21) en s'éloignant de la première surface (41), une seconde surface (42) qui est raccordée à un côté de la surface de raccordement (43) dans la direction circonférentielle (Dc), est formée dans une position plus éloignée de l'orifice d'aspiration (21) que la première surface (41), et est oblique par rapport à la surface de raccordement (43) de manière à s'approcher de l'orifice d'aspiration (21) en s'éloignant de la surface de raccordement (43), et une partie d'ouverture (81a) du passage d'alimentation en huile (81M) qui est formée sur la surface de raccordement (43),
    dans laquelle la surface de raccordement (43) comprend une première surface de raccordement (44) qui est parallèle à l'axe (A) et une seconde surface de raccordement (45) qui est raccordée au un côté (Da1) de la première surface de raccordement (44) dans la direction axiale (Da) et fait face à l'autre côté (Da2) dans la direction axiale (Da) et la partie d'ouverture (81a) du passage d'alimentation en huile (81M) est formée sur la seconde surface de raccordement (45), et
    dans lequel un angle obtus est formé entre la surface de raccordement (43) et la première surface (41).
  2. Compresseur à spirales de type ouvert selon la revendication 1,
    dans lequel l'orifice d'aspiration (21) est formé selon une forme tubulaire, et une partie d'une partie d'ouverture de l'orifice d'aspiration (21) et une partie de la partie d'ouverture du passage d'alimentation en huile (81M) se chevauchent lorsqu'elles sont observées dans une direction d'extension de l'orifice d'aspiration (21).
EP17198489.1A 2016-10-31 2017-10-26 Compresseur de type ouvert Active EP3315781B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2016213215A JP2018071459A (ja) 2016-10-31 2016-10-31 開放型圧縮機

Publications (2)

Publication Number Publication Date
EP3315781A1 EP3315781A1 (fr) 2018-05-02
EP3315781B1 true EP3315781B1 (fr) 2020-02-19

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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