EP0452896B1 - Système de lubrification pour compresseur à spirales - Google Patents

Système de lubrification pour compresseur à spirales Download PDF

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Publication number
EP0452896B1
EP0452896B1 EP91106116A EP91106116A EP0452896B1 EP 0452896 B1 EP0452896 B1 EP 0452896B1 EP 91106116 A EP91106116 A EP 91106116A EP 91106116 A EP91106116 A EP 91106116A EP 0452896 B1 EP0452896 B1 EP 0452896B1
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EP
European Patent Office
Prior art keywords
drive shaft
scroll
type compressor
lubricating oil
compressor
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.)
Expired - Lifetime
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EP91106116A
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German (de)
English (en)
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EP0452896A1 (fr
Inventor
Kazuto C/O Sanden Corporation Kikuchi
Yuji C/O Sanden Corporation Yoshii
Tsuyoshi C/O Sanden Corporation Fukui
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Sanden Corp
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Sanden Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
    • F04C18/02—Rotary-piston pumps specially adapted for elastic fluids of arcuate-engagement type, i.e. with circular translatory movement of co-operating members, each member having the same number of teeth or tooth-equivalents
    • F04C18/063—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 with coaxially-mounted members having continuously-changing circumferential spacing between them
    • 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

Definitions

  • This invention relates to a hermetically sealed scroll type refrigerant compressor, and more particularly to a lubricating mechanism thereof.
  • Japanese Patent Application Publication No. 60-73,083 discloses a hermetically sealed scroll type refrigerant compressor which is designed such that the longitudinal axis of a drive shaft is generally perpendicular to a horizontal plane when the compressor is installed. Therefore, in general, the compressor can be called a vertically installed type scroll refrigerant compressor.
  • the compressor includes a hermetically sealed housing in which a compression mechanism having a fixed and orbiting scrolls, a driving mechanism having a motor and a motor driven drive shaft, and a rotation preventing device for preventing rotation of the orbiting scroll during orbital motion are contained.
  • the fixed scroll includes a circular end plate which divides a cavity which is defined by the housing into a suction and discharge chamber sections.
  • the suction chamber section contains the driving mechanism, the rotation preventing mechanism and a spiral element of the fixed and orbiting scrolls.
  • the drive shaft includes an axial conduit of which the axis is radially shifted from the axis of the drive shaft.
  • the drive shaft is provided with a centrifugal pump at its lower end. The centrifugal pump is immersed in a reservoir of lubricating oil which accumulates at the inner bottom portion of the housing.
  • refrigerant gas flowing from an external fluid circuit flows into the suction chamber section through an inlet port which is disposed through a side wall of the housing, and is taken into a pair of outer fluid pockets which are defined by the spiral elements.
  • the refrigerant gas is compressed inwardly toward a central fluid pocket due to orbital motion of the orbiting scroll.
  • the compressed refrigerant gas in the discharge chamber section flows out of the compressor to the external fluid circuit through an outlet port which is disposed through an upper end of the housing. After circulating through the external fluid circuit, the refrigerant gas which exits through the outlet port returns to the compressor through the inlet port.
  • lubricating oil which accumulates at the inner bottom end portion of the housing flows upwardly through the axial conduit by virtue of operation of the centrifugal pump which operates during rotation of the drive shaft.
  • the lubricating oil which has upwardly passed over the axial conduit flows through other conduits, and into frictional surfaces of the slidable members of the compressor, such as the rotation preventing mechanism and the bearings rotatably supporting the drive shaft, in order to lubricate thereof.
  • the lubricating oil at the inner bottom portion of the housing is supplied to the frictional surfaces of the slidable members of the compressor through the axial conduit and the other conduits by use of the centrifugal pump.
  • flow rate of the lubricating oil which has passed over the axial conduit and the other conduits quadratically increases in accordance with increase in a rotational speed of the drive shaft, because that hydraulic resistance which is generated at the axial conduit and the other conduits when the lubricating oil passes therethrough is negligible.
  • Japanese Patent Application Publication No. 1-267376 discloses a vertically installed scroll refrigerant compressor, the construction of which being substantially similar to the construction of above cited Japanese '083 Publication.
  • this prior art device comprises throttling means formed by a pivotally arranged plate which is gradually blocking part of the area of the oil feed channel as the speed of rotation is increasing.
  • the pumping device is assembled by a large number of the component parts, thereby causing a complicated assembling process thereof and increasing manufacturing costs. Accordingly, it is an object of the present invention to provide a hermetically sealed scroll type refrigerant compressor which includes a simply structured lubricating mechanism for effectively lubricating the frictional surfaces of the slidable members thereof at any rotational speed of the drive shaft.
  • a scroll type compressor according to the invention is defined in claim 1.
  • Compressor 10 includes casing 11 comprising cylindrical portion 12 and a pair of shallow cup-shaped portions 13 and 14 hermetically fixed to both ends of cylindrical portion 12, fixed and orbiting scrolls 20 and 30, inner block member 40 and motor 50.
  • Cylindrical portion 12 includes annular flanges 121 and 122 radially outwardly projecting from an upper and lower end thereof, respectively.
  • Shallow cup-shaped portion 13 includes annular flange 131 radially outwardly projecting from an opening end thereof
  • shallow cup-shaped portion 14 includes annular flange 141 radially outwardly projecting from an opening end thereof.
  • Flange 131 is hermetically and releasably secured to flange 121 by a plurality of screws 200 through O-ring seal 201.
  • Flange 141 is hermetically and releasably secured to flange 122 by a plurality of screws 220 through O-ring seal 221. Thereby, cylindrical portion 12 and the par of shallow cup-shaped portions 13 and 14 are disassembled when is required.
  • Cylindrical portion 12 further includes a plurality of projections 123 radially inwardly projecting from the upper end thereof.
  • Fixed scroll 20 includes circular end plate 21 and spiral element or wrap 22 extending downwardly from the lower end surface of circular end plate 21.
  • Circular end plate 21 is forcibly inserted into an inner peripheral wall of shallow cup-shaped portion 13.
  • O-ring seal 210 is disposed between the outer peripheral surface of circular end plate 21 and the inner peripheral wall of shallow cup-shaped portion 13 to seal the mating surface therebetween.
  • the cavity defined by casing 11 is divided into first and second cavities 60 and 61 by circular end plate 21 of fixed scroll 20.
  • Axial hole 24 is formed in circular end plate 21 at the central location to link cavity 60 and a later-mentioned central fluid pocket 71b.
  • Axial hole 24 is covered by one way valve 25 disposed on the upper end surface of circular end plate 21.
  • Curved plate 251 of rigid material, such as, steel is disposed on one way valve 25 so as to prevent an excessive bend of one way valve 25. Curved plate 251 and one way valve 25 are firmly secured to circular end plate 21 at their one end by screw 26.
  • Circular end plate 21 is provided with annular wall 211 projecting downwardly from the peripheral end surface thereof.
  • Radial hole 23 is formed in annular wall 211.
  • Annular flange 211a radially outwardly projects from a lower end of annular wall 211.
  • Orbiting scroll 30 includes circular end plate 31 and spiral element or wrap 32 extending upwardly from one end surface of circular end plate 31.
  • Spiral element 22 of fixed scroll 20 and spiral element 32 of orbiting scroll 30 interfit at an angular and radial offset to form a plurality of line contacts which define at least one pair of sealed off fluid pockets 71 therebetween.
  • Annular projection 33 projects axially from the other end surface of circular end plate 31.
  • Shallow depression 34 is formed at the other end surface of circular end plate 31 at the central location, and is linked to radial conduit 101 which is formed in circular end plate 31.
  • Radial conduit 101 extends to the outer peripheral surface of circular end plate 31, but the outer radial end thereof is blocked by plug 102.
  • the outer radial portion of conduit 101 is linked through axial short path 103 to annular groove 104 formed at one end surface of circular end plate 31 at the peripheral location.
  • Radial conduit 101, axial short path 103 and annular groove 104 conduct the lubricating oil in shallow depression 34 to the mating surfaces between annular wall 211 of fixed scroll 20 and circular end plate 31 of orbiting scroll 30.
  • Inner block member 40 includes central portion 41, first axial annular wall 42 upwardly projecting from central portion 41 at a peripheral location, and second axial annular wall 43 downwardly projecting from central portion 41 at the peripheral location. Axially annular projection 44 projects downwardly from central portion 41 at a central location.
  • First axial annular wall 42 is secured by a plurality of screws 400 to flange 211a of annular wall 211.
  • a plurality of elongated screws 400a secure flange 211a to a plurality of projections 123, respectively through first axial annular wall 42.
  • Motor 50 includes stator 51 which is firmly secured to a lower end of second axial annular wall 43 by a plurality of screws 500.
  • Rotor 52 of motor 50 is disposed within stator 51 and is fixed to drive shaft 15 extending therethrough.
  • Wires 110 from stator 51 are connected with terminals 111 which are connected to an external electric source (not shown).
  • Hermetic seal base 120 is insulated from terminals 111 and hermetically fixed to opening 124 which is formed at cylindrical portion 12
  • Drive shaft 15 extends through axial annular projection 44.
  • Axial annular projection 44 extends within an opening in rotor 52.
  • Drive shaft 15 is rotatably supported within axial annular projection 44 through upper and lower fixed plain bearings 15a and 15b disposed between the exterior surface of drive shaft 15 and the interior surface of axial annular projection 44.
  • Drive shaft 15 extends through central portion 41 of inner block member 40.
  • Pin member 16 is integrated with and projects axially from the upper end surface of drive shaft 15. The axis of pin member 16 is radially offset from the axis of drive shaft 15.
  • Pin member 16 is rotatably disposed within axial annular projection 33 of orbiting scroll 30 through fixed plain bearing 16a.
  • Drive shaft 15 includes axial bore 151 extending from an opening at the lower end surface of drive shaft 15 and terminating at the lower end portion of pin member 16.
  • a plurality of radial bores 152 extend through drive shaft 15 at a location within annular projection 44.
  • Centrifugal pump 17 includes annular cylinder 171 which is firmly secured to the outer peripheral surface of the lower end portion of drive shaft 15 at its upper end by welding or by a plurality of fastening device, such as screws (not shown), and annular truncated cone 172 which is integrated with the lower end of annular cylinder 171. Annular truncated cone 172 gradually narrows downwardly. Centrifugal pump 17 is immersed in a reservoir of lubricating oil which accumulates at the inner bottom portion of casing 11.
  • a throttling device such as orifice tube 18 penetrates through pin member 16 so as to link shallow depression 34 to axial hole 151.
  • Balance weight 35 is integrated with a lower end portion of pin member 16 and serves to average the torque of drive shaft 15 acting on pin member 16 during rotation.
  • Balance weight 35 includes annular disk portion 35a and crescent-shaped portion 35b which is integrated with the upper surface of annular disk portion 35a.
  • Needle thrust bearing 81 is disposed between the end surface of axial annular projection 33 and the upper end surface of annular disk portion 35a, and needle thrust bearing 82 is disposed between the lower end surface of annular disk portion 35a and an upper surface of central portion 41 of inner block member 40. Thereby, balance weight 35 is rotatably supported by bearings 81 and 82.
  • Rotation preventing device 19 for example, an Oldham coupling mechanism is disposed between the lower peripheral surface of circular end plate 31, exterior of annular projection 33, and the upper surface of inner block member 40 to prevent rotation of orbiting scroll 30 during orbital motion.
  • Rotation preventing device 19 and pin member 16, as well as spiral elements 22 and 32, are all contained in cavity 61.
  • stator 51 In operation, stator 51 generates a magnetic field, causing rotation of rotor 52 to thereby rotate drive shaft 15. Rotation of drive shaft 15 is converted to orbital motion of orbiting scroll 30 by pin member 16, and rotational motion of orbiting scroll 30 is prevented by rotation preventing device 19.
  • Refrigerant gas is introduced into cavity 61 from the external refrigeration circuit through suction gas inlet pipe 90 and is taken into the outer of fluid pockets 71a between fixed scroll 20 and orbiting scroll 30 through hole 23. Refrigerant gas is compressed inwardly toward the central fluid pocket 71b of spiral elements 22 and 32 due to the orbital motion of orbiting scroll 30.
  • Lubricating oil which accumulates at the inner bottom portion of casing 11 flows upwardly through axial bore 151 by virtue of operation of centrifugal pump 17 which operates during rotation of drive shaft 15. Small part of the lubricating oil which upwardly flows through axial bore 151 further flows into the gap between fixed plain bearings 15a, 15b and the exterior surface of drive shaft 15 to lubricate the contact surfaces by virtue of the centrifugal force generated by rotation of drive shaft 15 during operation of the compressor. Large part of the lubricating oil which upwardly flows through axial bore 151 further flows through orifice tube 18.
  • the lubricating oil which has passed over orifice tube 18 is supplied to fixed plain bearings 16a, needle thrust bearings 81 and 82, and the mating surfaces between annular wall 211 of fixed scroll 20 and circular end plate 31 of orbiting scroll 30 in order to lubricate thereof.
  • flow rate of the lubricating oil which flows through axial bore 151 quadratically increases in accordance with increase in a rotational speed of drive shaft 15.
  • hydraulic friction generated at orifice tube 18 quadratically increases in accordance with increase in flow rate of the lubricating oil which flows through axial bore 151. Accordingly, increase in flow rate of the lubricating oil which has passed over orifice tube 18 is sufficiently declined due to the quadratic increase in hydraulic friction generated at orifice tube 18 even though flow rate of the lubricating oil which flows through axial bore 151 quadratically increases in accordance with increase in the rotational speed of drive shaft 15.
  • orifice tube 18 is used as a throttling device, however, a porous metal member or an aperture having a throttling portion can be also used as the throttling device in this invention.
  • Such the throttling devices can be positioned at any location along axial bore 151 of drive shaft 15.
  • the frictional surfaces of the slidable members of the compressor can receive an appropriate amount of the lubricating oil even though the drive shaft rotates in any rotational speed, while a lubricating mechanism is structured by a simple combination of the throttling device and the centrifugal pump. Accordingly, the defects met in JP-A-1-267376 are eliminated.

Claims (7)

  1. Compresseur (10) du type à serpentins ayant une carcasse étanche (11), ledit compresseur (10) comprenant un serpentin fixe (20) placé à l'intérieur de ladite carcasse, ledit serpentin fixe (20) comportant une première plaque d'extrémité (21) de laquelle s'étend un premier élément de spirale (22), un serpentin en mouvement orbital (30) comportant une seconde plaque d'extrémité (31) de laquelle s'étend un second élément de spirale (32), lesdits premier et second éléments de spirale (22, 32) s'emboîtant avec un certain décalage angulaire et radial pour former une pluralité de contacts linéaires qui délimitent au moins une paire de poches à fluide étanches (71), un mécanisme d'entraînement (15) fonctionnellement relié audit serpentin à mouvement orbital (30) pour créer ledit mouvement orbital dudit serpentin (30), un moyen (19) empêchant la rotation pour éviter la rotation dudit serpentin à mouvement orbital (30) au cours du mouvement orbital de façon que le volume desdites poches à fluide (71) varie afin de comprimer le fluide réfrigérant contenu dans lesdites poches, ledit mécanisme d'entraînement (15) comportant un arbre d'entraînement (15) supporté en rotation à l'intérieur de ladite carcasse, ledit arbre d'entraînement ayant un alésage (151) formé à l'intérieur, une extrémité dudit alésage étant plongée dans de l'huile de lubrification qui s'accumule à la partie intérieure inférieure de ladite carcasse, un moyen générateur de force centrifuge étant installé pour transporter ladite huile vers les sites à lubrifier et un moyen d'étranglement étant installé pour diminuer une augmentation de la quantité d'huile de lubrification aux vitesses supérieures, caractérisé en ce que le moyen d'étranglement (18) présente un frottement hydraulique qui augmente selon une loi quadratique avec la vitesse de circulation de ladite huile de lubrification.
  2. Compresseur du type à serpentins selon la revendication 1, dans lequel ledit moyen d'étranglement (18) comporte un orifice tubulaire.
  3. Compresseur du type à serpentins selon la revendication 1, dans lequel ledit moyen d'étranglement (18) comporte un organe métallique poreux.
  4. Compresseur du type à serpentins selon la revendication 1, dans lequel ledit moyen d'étranglement (18) comporte une ouverture ayant une partie d'étranglement.
  5. Compresseur du type à serpentins selon la revendication 1, dans lequel ledit moyen générateur de force centrifuge est constitué par une ouverture en tronc de cône (172) formée à une extrémité dudit alésage (151).
  6. Compresseur du type à serpentins selon la revendication 2, ledit mécanisme d'entraînement comprenant en outre un élément de broche (16) qui fait saillie dans la direction axiale d'une extrémité dudit arbre d'entraînement (15), l'axe de ladite broche étant décalé radialement par rapport à l'axe dudit arbre d'entraînement, ledit élément de broche (16) étant relié en rotation audit serpentin à mouvement orbital (30), ledit alésage (151) étant formé dans la direction axiale à travers ledit arbre d'entraînement (15) depuis une extrémité dudit arbre d'entraînement jusqu'à l'autre extrémité dudit arbre d'entraînement, ledit orifice tubulaire (18) pénétrant à travers ledit élément de broche (16).
  7. Compresseur du type à serpentins selon la revendication 1, dans lequel l'axe longitudinal dudit arbre d'entraînement (15) est généralement perpendiculaire à un plan horizontal lorsque le compresseur est installé.
EP91106116A 1990-04-17 1991-04-17 Système de lubrification pour compresseur à spirales Expired - Lifetime EP0452896B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2099414A JPH041485A (ja) 1990-04-17 1990-04-17 スクロール型圧縮機
JP99414/90 1990-04-17

Publications (2)

Publication Number Publication Date
EP0452896A1 EP0452896A1 (fr) 1991-10-23
EP0452896B1 true EP0452896B1 (fr) 1994-02-16

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EP91106116A Expired - Lifetime EP0452896B1 (fr) 1990-04-17 1991-04-17 Système de lubrification pour compresseur à spirales

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EP (1) EP0452896B1 (fr)
JP (1) JPH041485A (fr)
KR (1) KR100192699B1 (fr)
AU (1) AU640218B2 (fr)
CA (1) CA2040721A1 (fr)
DE (1) DE69101168T2 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7861541B2 (en) 2004-07-13 2011-01-04 Tiax Llc System and method of refrigeration

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR100924895B1 (ko) 2002-05-24 2009-11-02 파나소닉 주식회사 스크롤 압축기
JP2005083290A (ja) * 2003-09-10 2005-03-31 Fujitsu General Ltd スクロール圧縮機
DE102019005095A1 (de) * 2019-07-23 2021-01-28 KSB SE & Co. KGaA Pumpenanordnung mit einem Schmier- und Kühlsystem

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0673083A (ja) * 1992-08-28 1994-03-15 Takara Shuzo Co Ltd 新規糖質分解酵素インヒビター

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0673083A (ja) * 1992-08-28 1994-03-15 Takara Shuzo Co Ltd 新規糖質分解酵素インヒビター

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7861541B2 (en) 2004-07-13 2011-01-04 Tiax Llc System and method of refrigeration

Also Published As

Publication number Publication date
DE69101168T2 (de) 1994-07-21
EP0452896A1 (fr) 1991-10-23
KR100192699B1 (ko) 1999-06-15
DE69101168D1 (de) 1994-03-24
AU640218B2 (en) 1993-08-19
KR920005749A (ko) 1992-04-03
CA2040721A1 (fr) 1991-10-18
JPH041485A (ja) 1992-01-06
AU7438991A (en) 1991-11-07

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