EP0468238B1 - Compresseur à spirales avec mécanisme de déplacement variable - Google Patents

Compresseur à spirales avec mécanisme de déplacement variable Download PDF

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Publication number
EP0468238B1
EP0468238B1 EP91111058A EP91111058A EP0468238B1 EP 0468238 B1 EP0468238 B1 EP 0468238B1 EP 91111058 A EP91111058 A EP 91111058A EP 91111058 A EP91111058 A EP 91111058A EP 0468238 B1 EP0468238 B1 EP 0468238B1
Authority
EP
European Patent Office
Prior art keywords
fluid
scroll
end plate
pair
chamber
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
Application number
EP91111058A
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German (de)
English (en)
Other versions
EP0468238A1 (fr
Inventor
Yasuyuki c/o Sanden Corporation Matsudaira
Atsushi c/o Sanden Corporation Mabe
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Sanden Corp
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Sanden Corp
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Publication date
Application filed by Sanden Corp filed Critical Sanden Corp
Publication of EP0468238A1 publication Critical patent/EP0468238A1/fr
Application granted granted Critical
Publication of EP0468238B1 publication Critical patent/EP0468238B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C27/00—Sealing arrangements in rotary-piston pumps specially adapted for elastic fluids
    • F04C27/005—Axial sealings for working fluid

Definitions

  • the present invention relates to a scroll type compressor. More particularly, the present invention relates to a scroll type compressor with a variable displacement mechanism.
  • Scroll type fluid displacement apparatus are well known in the prior art.
  • U.S. Pat. No. 801, 182 issued to Cruex discloses such an apparatus which includes two scrolls, each having a circular end plate and a spiroidal or involute spiral element.
  • the scrolls are maintained angularly and radially offset so that both spiral elements interfit to form a plurality of line contacts between their spiral curved surfaces to thereby seal off and define at least one pair of fluid pockets.
  • the relative orbital motion of the two scrolls shifts the line contacts along the spiral curved surfaces and, as a result, the volume of the fluid pockets increases or decreases, dependent on the direction to the orbital motion.
  • a scroll type fluid displacement apparatus may be used to compress, expand or pump fluids.
  • Mechanisms to control the compression ratio generally have used a pair of holes through the end plate of one of the scrolls, with the pair of holes providing controlled communication to a chamber which is located on the opposite side to the spiral element with respect to the end plate.
  • the pair of circular holes provide controlled communication to an intermediate pressure chamber.
  • an axial tip seal element is disposed in the groove which is located along the axial end of each of the spiral elements in order to sufficiently maintain the axial sealing between the axial end surface of the spiral elements and the inner surface of the end plates.
  • the intermediately compressed fluid which flows from the sealed off pockets to the intermediate pressure chamber through the pair of circular holes controllably flows back to the suction chamber via a communication channel formed at the end plate in response to operation of a communication control mechanism.
  • pressure in the intermediate pressure chamber varies from the suction pressure to the certain pressure which can prevent the communication between the sealed off fluid pockets and the intermediate pressure chamber so that the compression ratio of the compressor is controlled in the range from the maximum value, i.e., 100 % to the predetermined minimum value, e.g., 30 %.
  • the minimum value of compression ratio is undesirably increased because that the value of the pressure drop at the pair of circular holes becomes not negligible due to extreme increase in flow rate of the fluid which passes through the pair of circular holes. Accordingly, controllability of the displacement adjusting mechanism becomes decreased, in particular, in operation of the compressor in the high rotational speed.
  • a radius of the pair of circular holes can be enlarged within the value, which is slightly smaller than thickness of the spiral elements, so as to reduce the pressure drop at the pair of circular holes to the negligible value.
  • a certain portion of the axial end of the spiral element of one of the scrolls passes over the circular hole in a situation when the diameter of the circular hole is enlarged, a certain portion of the axial tip seal element locating on the circular hole during relative orbital motion of the scrolls easily tends to bend toward the opening of the circular hole because of increase in lack of support caused by an enlargement of the blank which is defined by the circular hole.
  • the certain portion of the axial tip seal element easily tends to be bitten by an edge of the axial end of the spiral element and an edge of the circular hole. Thereby, the axial tip seal element is damaged, such as cutting thereof, so that the function of the compression mechanism of the compressor becomes decreased.
  • EP-A-49480 discloses a scroll type compressor without displacement adjusting means but with a discontinuous seal element.
  • the discontinuous seal prevents concentrated wear of the seal due to back pressure acting on it.
  • a scroll type compressor according to the present invention is defined in claim 1.
  • Figure 1 is a vertical longitudinal sectional view of a scroll type compressor with a variable displacement mechanism in accordance with one embodiment of this invention.
  • Figure 2 is a schematic horizontal perspective view of the scroll type compressor of Figure 1, viewing from the right side in Figure 1.
  • the scroll type compressor includes a compressor housing 10 having a front end plate 11 and a cup-shaped casing 12 which is attached to front end plate 11.
  • An opening 111 is formed in the center of the front end plate 11 and a drive shaft 13 is disposed in the opening 111.
  • An annular projection 112 is formed in a rear surface of the front end plate 11.
  • An annular projection 112 faces cup-shaped casing the 12 and is concentric with opening the 111.
  • An outer peripheral surface of the projection 112 extends into an inner wall of an opening 121 of the cup-shaped casing 12.
  • the opening 121 of the cup-shaped casing 12 is covered by the front end plate 11.
  • An O-ring 14 is placed between the outer peripheral surface of the annular projection 112 and an inner wall of the opening 121 of the cup-shaped casing 12 to seal the mating surface of the front end plate 11 and the cup-shaped casing 12.
  • An annular sleeve 16 longitudinally projects from a front end surface of the front end palte 11, surrounds the drive shaft 13, and defines a shaft seal cavity 161.
  • the drive shaft 13 is rotatably supported by an annular sleeve 16 through a bearing 17 located within the front end of sleeve 16.
  • the drive shaft 13 has a disk-shaped rotor 131 at its inner end which is rotatably supported by the front end plate 11 through a bearing 15 located within the opening 111 of the front end plate 11.
  • a shaft seal assembly 18 is coupled to the drive shaft 13 within the shaft seal cavity 161 of annular sleeve 16.
  • a pulley 201 is rotatably supported by a ball bearing 19 which is carried on the outer peripheral surface of the annular sleeve 16.
  • An electromagnetic coil 202 is fixed about the outer surface of the annular sleeve 16 by a support plate 204.
  • An armature plate 203 is elastically supported on the outer end of the drive shaft 13.
  • the pulley 201, the electromagnetic coil 202 and the armature plate 203 form an electromagnetic clutch 20.
  • the drive shaft 13 driven by an external power source, for example, the engine of an automobile, through a rotation transmitting device such as the electromagnetic clutch 20.
  • a fixed scroll 21, an orbiting scroll 22 and a rotation preventing/thrust bearing mechanism 24 for the orbiting scroll 22 are disposed in the interior of the housing 10.
  • the fixed scroll 21 includes a circular end plate 211 and a spiral element 212 affixed to or extending from one end surface of the circular end plate 211.
  • the fixed scroll 21 is fixed within the inner chamber of the cup-shaped casing 12 by screws (not shown) screwed into the end plate 211 from the outside of the cup-shaped casing 12.
  • An O-ring 123 is disposed between an outer peripheral surface of the circular end plate 211 and an inner peripheral wall of the cup-shaped casing 12. Therefore, the circular end plate 211 of the fixed scroll 21 insulatingly partitions the inner chamber of the cup-shaped casing 12 into two chambers, a front chamber 27 and a rear chamber 28.
  • the spiral element 212 of the fixed scroll 21 is located within the front chamber 27.
  • a wall 122 longitudinally projects from the inner end surface of the cup-shaped casing 12 to device the rear chamber 28 into a discharge chamber 281 and an intermediate pressure chamber 282.
  • the end surface of wall 122 contacts the rear end surface of the circular end plate 211.
  • the orbiting scroll 22 which is located in the front chamber 27, includes a circular end plate 221 and a spiral element 222 extending from one end surface of the circular end plate 221.
  • the spiral element 222 of the orbiting scroll 22 and the spiral element 212 of the fixed scroll 21 interfit at an angular offset of approximately 180° and a predetermined radial offset, to form sealed spaces between the spiral element 212 and 222.
  • the orbiting scroll 22 is rotatably supported by a bushing 23, which is eccentrically connected to the inner end of a disc-shaped portion 131, through a radial needle bearing 30. While the orbiting scroll 22 orbits, rotation of the orbiting scroll 22 is prevented by a rotation preventing/thrust bearing mechanism 24 which is placed between the rear end surface of the front end plate 11 and the circular end plate 221 of the orbiting scroll 22.
  • the compressor housing 10 is provided with an inlet port 31 and an outlet port 32 for connecting the compressor to an external refrigeration circuit.
  • Refrigeration fluid from the external circuit is introduced into a suction chamber 271 through the inlet port 31 and flows into sealed formed between the spiral elements 212 and 222 through open spaces between the spiral elements.
  • the sealed spaces between the spiral elements sequentially open and close during the orbital motion of the orbiting scroll 22. When these spaces are open, fluid to be compressed flows into these spaces but no compression occurs. When these spaces are closed, no additional fluid flows into these spaces and compression begins. Since the location of the outer terminal ends of the spiral elements 212 and 222 is at a final involute angle, location of the spaces is directly related to the final involute angle.
  • refrigeration fluid in the sealed space is moved radially inwardly and is compressed by the orbital motion of the orbiting scroll 22.
  • Compressed refrigeration fluid at a center sealed space 272 is discharged to the discharge chamber 281 past a valve plate 231 of spring material through a discharge port 213 which is formed at the center of the circular end plate 211.
  • a valve retainer 231a receives the valve plate 231 to prevent excessive bending of the valve plate 231. Excessive bending of the valve plate 231 can cause damage to the valve plate 231.
  • a pair of circular holes 214 and 215 are formed in the circular end plate 211 of fixed scroll 21 and are generally symmetrically placed so that an axial end surface of the spiral element 222 of the orbiting scroll 22 generally simultaneously crosses over both holes.
  • the holes 214, 215 communicate between an intermediate sealed space 273 and an intermediate pressure chamber 282.
  • a radius of each of the holes 214, 215 is designed so as to be slightly smaller than thickness of the spiral elements.
  • the circular hole 214 opens along the inner side wall of the spiral element 212.
  • the circular hole 215 opens along the outer side wall of the spiral element 212.
  • valve plate 341 A pair of valve plates (only one valve plate is shown in Figure 1 as valve plate 341) are attached by fasteners (not shown) to the rear end surface of the circular end plate 211.
  • valve plate 341 and the other valve plate are made of spring material so that the bias of the valve plate 341 and the other valve plate push them against a rear end opening of the hole 214 and the other hole to close hole.
  • a pair of valve retainers (only one valve retainer is shown in Figure 1 as valve retainer 341a) which are associated with the valve plates function as well as a valve retainer 231a.
  • the circular end plate 211 of the fixed scroll 21 also has a communicating channel 29 formed at an outer side portion of the terminal end of the spiral element 212.
  • the communicating channel 29 is provided for communication between the suction chamber 271 and the intermediate pressure chamber 282.
  • a control mechanism 36 controls fluid communication between the suction chamber 271 and the intermediate pressure chamber 282.
  • An axial tip seal element 230 is disposed in a groove 213 which is located along the axial end of the spiral element 212 of the fixed scroll 21.
  • a plurality of axial tip seal elements 240a, 240b and 240c are disposed in a plurality of grooves 223a, 223b, 223c, which are located along the axial end of the spiral element 222 of the orbiting scroll 22 in series, respectively.
  • the axial tip seal elements 240a and 240b define a first spaced portion 241 at the axial end of the spiral element 222 of the orbiting scroll 22.
  • the axial tip seal elements 240b and 240c define a second spaced portion 242 at the axial end of the spiral element 222 of the orbiting scroll 22.
  • first and second spaced portions 241 and 242 are provided with no groove and no axial tip seal element.
  • the first and second spaced portions 241 and 242 are positioned so as to cross over the circular holes 214 and 215 respectively during the orbital motion of the orbiting scroll 22.
  • the axial tip seal element 204a, 204b and 204c define the first and second spaced portions 241 and 242 the axial sealing between the axial end surface of the spiral element 222 of the orbiting scroll 22 and the inner surface of the circular end plate 211 of the fixed scroll 21 can be negligibly spoiled.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)

Claims (4)

  1. Compresseur à fluide du type à spirales, comprenant une enveloppe (10) ayant un orifice d'entrée de fluide (31) et un orifice de sortie de fluide (32), une spirale fixe (21) disposée en position fixe dans l'enveloppe (10) et ayant un flasque d'extrémité (211) sur lequel un premier enroulement spiral (212) s'élève en faisant saillie dans la cavité intérieure de ladite enveloppe (10), une spirale orbitante (22) ayant un flasque (221) sur lequel s'élève un deuxième enroulement spiral (222), lesdits premier et second enroulements (221,222) étant emboîtés l'un dans l'autre avec un certain décalage angulaire et radial pour former une pluralité de contacts linéaires qui définissent au moins une paire de poches à fluide fermées, des moyens de réglage du déplacement comprenant au moins deux trous (214,215) formés à travers ledit flasque (211) de l'une (21) des spirales, pour former un premier canal de fluide entre ladite paire au moins de poches de fluide fermées et la face dudit flasque (211) de ladite première spirale (21) qui est à l'opposé de son enroulement respectif (212),
    caractérisé par au moins trois éléments d'étanchéité (240a,240b,240c) placés le long de la surface d'extrémité axiale d'au moins l'enroulement (222) de l'autre (22) desdites spirales en série, lesdits au moins trois éléments d'étanchéité (240a,240b,240c) définissant entre eux au moins deux parties espacées, lesdites au moins deux parties espacées étant positionnées de manière à croiser ladite au moins une paire de trous (214,215) pendant le mouvement orbital relatif desdites spirales (21,22).
  2. Compresseur du type à spirales selon la revendication 1, comprenant un mécanisme d'entraînement relié fonctionnellement à ladite spirale orbitante (22) pour déterminer le mouvement orbital de celle-ci, des moyens (24) d'interdiction de la rotation destinés à empêcher ladite spirale orbitante (22) de tourner pendant son mouvement orbital, de telle manière que le volume des poches de fluide varie pendant le mouvement orbital pour comprimer le fluide dans les poches, et le fluide comprimé issu d'une poche de fluide centrale (272) formée par lesdites spirales (21,22) est refoulé à travers une ouverture de sortie formée dans l'un desdits flasques (211,221).
  3. Compresseur du type à spirales selon la revendication 1 ou 2, dans lequel ladite au moins une paire de trous (214,215) sont circulaires.
  4. Compresseur du type à spirales selon une quelconque des revendications 1 à 3, dans lequel ledit flasque circulaire (211) de ladite spirale fixe (21) divise l'intérieur de ladite enveloppe (10) en une chambre avant (27) et une chambre arrière (28), ladite chambre avant (27) communiquant avec ledit orifice d'entrée de fluide (31) et ladite chambre arrière (28) étant divisée en une chambre de refoulement (281) qui établit la communication entre ledit orifice de sortie de fluide (32) et ladite poche de fluide centrale (272), et une chambre de pression intermédiaire (282), ledit premier canal de fluide étant formé entre les poches de fluide et ladite chambre de pression intermédiaire (282), un canal de communication étant formé à travers ledit flasque (211) de ladite spirale fixe (21) pour former un second canal de fluide entre ladite chambre de pression intermédiaire (282) et ladite chambre avant (27).
EP91111058A 1990-07-05 1991-07-03 Compresseur à spirales avec mécanisme de déplacement variable Expired - Lifetime EP0468238B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2176300A JPH0466793A (ja) 1990-07-05 1990-07-05 容量可変型スクロール圧縮機
JP176300/90 1990-07-05

Publications (2)

Publication Number Publication Date
EP0468238A1 EP0468238A1 (fr) 1992-01-29
EP0468238B1 true EP0468238B1 (fr) 1993-10-06

Family

ID=16011180

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91111058A Expired - Lifetime EP0468238B1 (fr) 1990-07-05 1991-07-03 Compresseur à spirales avec mécanisme de déplacement variable

Country Status (6)

Country Link
EP (1) EP0468238B1 (fr)
JP (1) JPH0466793A (fr)
KR (1) KR100193914B1 (fr)
AU (1) AU634895B2 (fr)
CA (1) CA2046245C (fr)
DE (1) DE69100471T2 (fr)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5458879A (en) * 1994-03-03 1995-10-17 The Procter & Gamble Company Oral vehicle compositions
JP4103225B2 (ja) * 1998-06-24 2008-06-18 株式会社日本自動車部品総合研究所 圧縮機
JP2002130156A (ja) * 2000-10-20 2002-05-09 Anest Iwata Corp 多段式流体圧縮部を備えたスクロール流体機械
KR102310647B1 (ko) 2014-12-12 2021-10-12 삼성전자주식회사 압축기

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CA1222986A (fr) * 1980-09-30 1987-06-16 Kiyoshi Terauchi Compresseur centrifuge
JPH0756274B2 (ja) * 1987-03-20 1995-06-14 サンデン株式会社 スクロール式圧縮機

Also Published As

Publication number Publication date
CA2046245A1 (fr) 1992-01-06
EP0468238A1 (fr) 1992-01-29
JPH0466793A (ja) 1992-03-03
AU8013791A (en) 1992-01-09
KR100193914B1 (ko) 1999-06-15
DE69100471T2 (de) 1994-03-03
AU634895B2 (en) 1993-03-04
DE69100471D1 (de) 1993-11-11
CA2046245C (fr) 1998-11-17
KR920002935A (ko) 1992-02-28

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