EP1087141A2 - Spiralverdichter - Google Patents

Spiralverdichter Download PDF

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Publication number
EP1087141A2
EP1087141A2 EP00120916A EP00120916A EP1087141A2 EP 1087141 A2 EP1087141 A2 EP 1087141A2 EP 00120916 A EP00120916 A EP 00120916A EP 00120916 A EP00120916 A EP 00120916A EP 1087141 A2 EP1087141 A2 EP 1087141A2
Authority
EP
European Patent Office
Prior art keywords
seal member
scroll
movable
rotary shaft
base plate
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.)
Withdrawn
Application number
EP00120916A
Other languages
English (en)
French (fr)
Other versions
EP1087141A3 (de
Inventor
Kazuhiro Kuroki
Hiroyuki Gennami
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.)
Toyota Industries Corp
Original Assignee
Toyota Industries Corp
Toyoda Jidoshokki Seisakusho KK
Toyoda Automatic Loom Works Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Toyota Industries Corp, Toyoda Jidoshokki Seisakusho KK, Toyoda Automatic Loom Works Ltd filed Critical Toyota Industries Corp
Publication of EP1087141A2 publication Critical patent/EP1087141A2/de
Publication of EP1087141A3 publication Critical patent/EP1087141A3/de
Withdrawn legal-status Critical Current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
    • 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

Definitions

  • the present invention relates to a scroll-type compressor, more particularly, to a sealing structure of scroll-type compressors.
  • Japanese Unexamined Patent Publication No. 4-175483 discloses a scroll-type compressor shown in Fig. 8.
  • the compressor includes a movable scroll 61 and a stationary scroll 65.
  • the scrolls 61, 65 each have a volute portion to compress refrigerant gas.
  • the movable scroll 61 includes a base plate 62.
  • a groove 63 is formed in the base plate 62 on the surface from which the volute portion extends.
  • the groove 63 is filled with a filler 64.
  • the filler 64 forms a seal between the stationary scroll 65 and the movable scroll 61.
  • the filler 64 is located in a surface of the base plate 62 that faces the stationary scroll 65, the area of contact between the scrolls 65 and 61 must be relatively large.
  • the sealing structure of the prior art publication is used in a scroll-type compressor that includes a discharge port formed in the movable scroll, the diameter of the base plate of the movable scroll will be relatively great, which will increase the overall size of the compressor.
  • the discharge port communicates with a space that is defined adjacent to the movable scroll. Specifically, the space is defined at a side of the movable scroll that is opposite to the volute portion. Therefore, the pressure of the compressed refrigerant gas acts on the movable scroll. If excessive, the load of the pressure hinders smooth orbital motion of the movable scroll, which makes the movable scroll less reliable and reduces the life of the movable scroll.
  • a first objective of the present invention to provide a scroll type compressor having a sealing structure that has high sealing characteristics between a movable scroll and a stationary scroll and reduces the radial dimension of a scroll-type compressor in which a discharge port is formed in a movable scroll.
  • a second objective of the present invention is to reduce excessive load acting on a side of the movable scroll opposite to a volute portion.
  • a scroll-type compressor includes a housing, a projection extending inward from the inner surface of the housing, a rotary shaft, an eccentric shaft, a stationary scroll, a movable scroll and a seal member.
  • the rotary shaft is supported by the housing to rotate about its axis.
  • the eccentric shaft extends from the rotary shaft.
  • the axis of the eccentric shaft is offset from the axis of the rotary shaft.
  • the stationary scroll is fixed to the housing and includes a base stationary plate and a stationary volute portion extending from the base plate.
  • the movable scroll includes a movable base plate and a movable volute portion extending from the movable base plate.
  • the two volute portions cooperate to form a variable displacement pocket between the two scrolls.
  • a discharge port is formed in the movable scroll. Rotation of the rotary shaft is converted into orbital movement of the movable scroll by the eccentric shaft. Gas is introduced into the pocket, compressed in the pocket and discharged to a discharge chamber, which is radially inside the projection, through the discharge port in accordance with the orbital movement of the movable scroll.
  • the seal member substantially prevents gas that is discharged from the discharge port from flowing out from the discharge chamber radially inside the projection.
  • the seal member is located between the movable base plate and the projection, and further inward than the outermost inner surface of the stationary scroll.
  • a stationary scroll 11 is secured to a center housing member 12.
  • a motor housing member 13 is also secured to the center housing member 12.
  • a rotary shaft 14 is supported by the center housing member 12 and the motor housing member 13 through radial bearings 15, 16.
  • An eccentric shaft 17 is formed integrally with the rotary shaft 14.
  • the inner wall of the motor housing member 13 and the center housing member 12 define a motor chamber 18.
  • a counterweight 19 and a bushing 20 are supported by the eccentric shaft 17.
  • the rotary shaft 14, the eccentric shaft 17 and the bushing 20 rotate integrally.
  • a movable scroll 21 is supported by the bushing 20 through a needle bearing 22.
  • the movable scroll 21 includes a movable base plate 23 and a movable volute portion 24 that extends from the movable base plate 23.
  • the stationary scroll 11 includes a stationary base plate 25 and a stationary volute portion 26 that extends from the stationary base plate 25.
  • the volute portions 24, 26 engage each other.
  • a boss 27 extends from the movable base plate 23 at the side opposite to the movable volute portion 24.
  • the needle bearing 22 is accommodated in the boss 27.
  • the base plates 23, 25 and the volute portions 24, 26 define pockets 28. As the movable scroll 21 orbits, each pocket 28 moves radially inward while its volume decreases.
  • Recesses 29, the number of which is four in this embodiment, are formed in a side of the center housing member 12 that faces the stationary scroll 11.
  • the recesses 29 are arranged circumferentially.
  • a ring 30 is located in each recess 29.
  • a fixed pin 31 is fixed in each recess 29.
  • Movable pins 32 are fixed to the movable scroll 21. The number and the locations of the movable pins 32 correspond to those of the recesses 29.
  • Each fixed pin 31 and the corresponding movable pin 32 are inserted into the corresponding ring 30.
  • the rings 30, the fixed pins 31 and the movable pins 32 prevent the movable scroll 21 from rotating about its own axis.
  • a stator 33 is fixed to the inner wall of the motor housing member 13.
  • a rotor 34 is fixed to the rotary shaft 14 at a location corresponding to the stator 33.
  • the stator 33 and the rotor 34 form an electric motor. When a current is supplied to the stator 33, the rotor 34 and the rotary shaft 14 rotate integrally.
  • a discharge port 35 is formed substantially in the center of the movable base plate 23.
  • the movable base plate 23 also has a float valve 36 at a position corresponding to the discharge port 35.
  • the discharge port 35 is connected to the interior of the boss 27, or a discharge chamber 37, through the float valve 36.
  • a first passage 38 is formed in the rotary shaft 14 in the vicinity of the bearing 15.
  • a second passage 39 is formed in the rotary shaft 14 in the vicinity of the bearing 16 to connect the motor chamber 18 to the exterior of the motor housing member 13.
  • a projection 42 is formed in the center housing member 12 and extends radially inward from the inner surface of the center housing member 12.
  • the projection 42 is adjacent to the movable scroll 21 and is on the opposite side of the movable base plate 23 from the movable volute portion 24.
  • the projection 42 extends radially further inward than the outermost inner surface 43 of the stationary scroll 11.
  • an annular groove 45 is formed in a surface of the projection 42 that faces the movable scroll 21.
  • the groove 45 has a rectangular cross section.
  • a seal member 46 which is illustrated in Fig. 2, is located in the groove 45.
  • the outer diameter D S of the seal member 46 is slightly smaller than the outer diameter D G of the annular groove 45.
  • the radial dimension W G of the groove 45 is slightly greater than the radial dimension W S of the seal member 46.
  • the axial dimension P of the groove 45 is slightly smaller than the axial dimension T of the seal member 46.
  • the seal member 46 axially protrudes from the groove 45.
  • the seal member 46 is movable in the groove 45 in the axial direction of the rotary shaft 14.
  • the interior of the projection 42, or the space radially inside the seal member 46, is connected to the discharge chamber 37 through the bearing 22 and is exposed to the discharge pressure.
  • the space in the projection 42 will be referred to as a high pressure chamber 44.
  • the space that is between the projection 42 and the movable scroll 21 and the space outside the seal member 46 are exposed to a pressure that is close to the suction pressure.
  • the spaces will therefore be referred to as a low pressure chamber 47.
  • the pressure difference between the high pressure chamber 44 and the low pressure chamber 47 urges the seal member 46 to the position shown in Fig. 3, or to a seal position.
  • the sealing structure of Figs. 1 to 3 has the following advantages.
  • each seal member 46, 50 may be adjustable.
  • each of the seal members 46, 50 may be replaced by a seal member that has a slant cut.
  • a seal member 53 illustrated in Figs. 7(a) and 7(b) is an example of such a seal member.
  • Two seal members 53 having different sizes are prepared to replace the seal members 46, 50.
  • the cut portion 52 is deformed as shown in Fig. 7(b) by a pressure difference between the high pressure area and the low pressure area. The deformation permits the seal member 53 to contact the outer wall of the grooves 45, 49 and dimensional errors in the grooves 45, 49 are absorbed.
  • the seal member 53 may be formed by rubber that is treated to reduce friction.
  • the grooves 45, 49 may be formed in the side of the movable scroll 21 that is opposite to the movable volute portion 24.
  • two or more intermediate pressure chambers may be formed.
  • the number of annular sealing members is also increased, which properly seals the high pressure chamber 44 from the low pressure chamber 47.
  • the second seal member 50 need not be located between the bushing and the movable scroll 21.
  • the diameter of the eccentric shaft 17 may be increased, and the second seal member 50 may be located between the eccentric shaft 17 and the movable scroll 21.
  • a passage for directly communicating the discharge chamber 37 with the exterior of the housing may be formed in the rotary shaft 14.
  • the third seal member 48 which is located between the rotary shaft 14 and the center housing 12, may be omitted.
  • the first seal member 46 may be axially aligned with the outermost inner surface 43 of the stationary scroll 11. This structure also permits the size of the compressor to be reduced.
  • the third seal member 48 may be replaced with a lip seal. Alternatively, the third seal member 48 may be omitted and the bearing 15 may be replaced by a bearing with a seal.
  • the sealing structure of the present invention may be embodied in other types of scroll-type compressors, for example, in a scroll-type compressor that is driven by an engine.
  • a scroll-type compressor having an improved seal structure includes a stationary scroll (11) and a movable scroll (21). Gas is discharged to an inner zone (44) through a discharge port (35) in accordance with orbital movement of the movable scroll (21).
  • the seal structure includes a seal member (46), which is located between a movable base plate (23) and a radial projection (42).
  • the seal member (46) substantially prevents gas that is discharged from the discharge port (35) from flowing radially from the zone (44).
  • the seal member (46) is moved axially by the force of gas pressure.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP00120916A 1999-09-27 2000-09-26 Spiralverdichter Withdrawn EP1087141A3 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP27286399 1999-09-27
JP27286399A JP2001090680A (ja) 1999-09-27 1999-09-27 スクロール型圧縮機のシール構造

Publications (2)

Publication Number Publication Date
EP1087141A2 true EP1087141A2 (de) 2001-03-28
EP1087141A3 EP1087141A3 (de) 2002-04-03

Family

ID=17519827

Family Applications (1)

Application Number Title Priority Date Filing Date
EP00120916A Withdrawn EP1087141A3 (de) 1999-09-27 2000-09-26 Spiralverdichter

Country Status (2)

Country Link
EP (1) EP1087141A3 (de)
JP (1) JP2001090680A (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6464481B2 (en) 2000-09-29 2002-10-15 Kabushiki Kaisha Toyota Jidoshokki Scroll compressors
US6568928B2 (en) * 2000-12-28 2003-05-27 Kabushiki Kaisha Toyota Jidoshokki Scroll-type compressor

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP7262013B2 (ja) * 2019-09-05 2023-04-21 パナソニックＩｐマネジメント株式会社 スクロール圧縮機

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04175483A (ja) 1990-11-07 1992-06-23 Hitachi Ltd スクロール圧縮機

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4552518A (en) * 1984-02-21 1985-11-12 American Standard Inc. Scroll machine with discharge passage through orbiting scroll plate and associated lubrication system
US4928503A (en) * 1988-07-15 1990-05-29 American Standard Inc. Scroll apparatus with pressure regulation
US4992032A (en) * 1989-10-06 1991-02-12 Carrier Corporation Scroll compressor with dual pocket axial compliance
JP3028642B2 (ja) * 1991-06-27 2000-04-04 ダイキン工業株式会社 スクロール形流体機械
JP2956509B2 (ja) * 1995-01-17 1999-10-04 松下電器産業株式会社 スクロール気体圧縮機
US5593295A (en) * 1995-04-19 1997-01-14 Bristol Compressors, Inc. Scroll compressor construction having an axial compliance mechanism

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH04175483A (ja) 1990-11-07 1992-06-23 Hitachi Ltd スクロール圧縮機

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6464481B2 (en) 2000-09-29 2002-10-15 Kabushiki Kaisha Toyota Jidoshokki Scroll compressors
US6568928B2 (en) * 2000-12-28 2003-05-27 Kabushiki Kaisha Toyota Jidoshokki Scroll-type compressor

Also Published As

Publication number Publication date
EP1087141A3 (de) 2002-04-03
JP2001090680A (ja) 2001-04-03

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