EP0467342B1 - Compresseur à spirales - Google Patents

Compresseur à spirales Download PDF

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Publication number
EP0467342B1
EP0467342B1 EP91111968A EP91111968A EP0467342B1 EP 0467342 B1 EP0467342 B1 EP 0467342B1 EP 91111968 A EP91111968 A EP 91111968A EP 91111968 A EP91111968 A EP 91111968A EP 0467342 B1 EP0467342 B1 EP 0467342B1
Authority
EP
European Patent Office
Prior art keywords
counterweight
scroll member
housing
intake port
movable scroll
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
EP91111968A
Other languages
German (de)
English (en)
Other versions
EP0467342A1 (fr
Inventor
Yuyi C/O Kabushiki Kaisha Toyoda Izumi
Tetsuhiko C/O Kabushiki Kaisha Toyoda Fukanuma
Tetsuo C/O Kabushiki Kaisha Toyoda Yoshida
Tatsushi C/O Kabushiki Kaisha Toyoda Mori
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
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 Toyoda Jidoshokki Seisakusho KK, Toyoda Automatic Loom Works Ltd filed Critical Toyoda Jidoshokki Seisakusho KK
Publication of EP0467342A1 publication Critical patent/EP0467342A1/fr
Application granted granted Critical
Publication of EP0467342B1 publication Critical patent/EP0467342B1/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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/12—Arrangements for admission or discharge of the working fluid, e.g. constructional features of the inlet or outlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • 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
    • 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
    • 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
    • F04C2250/00—Geometry
    • F04C2250/10—Geometry of the inlet or outlet
    • F04C2250/101—Geometry of the inlet or outlet of the inlet
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2250/00—Geometry
    • F05B2250/50—Inlet or outlet
    • F05B2250/501—Inlet

Definitions

  • the present invention relates to a scroll type compressor suitable for an automobile air conditioner, more particularly, to an improvement thereof of the lubrication for a sealing means, bearings, and an anti-spin mechanism.
  • a small size scroll type compressor suitably used for an automobile air conditioner is disclosed in Japanese Unexamined Patent Publication No. 57-62988.
  • this scroll type compressor (hereinafter referred to as "compressor"), as shown in Fig. 4, a stationary scroll member 52 comprising a stationary side plate 521 and a stationary spiral body 522 is fixed to a housing half 51, and movable scroll member 54 comprising a movable side plate 541 and a movable spiral body 542 is arranged in the housing half 51 and other housing half 53.
  • the movable scroll member 54 is engaged with the fixed scroll member 52, and thus a plurality of compression chambers 56 are formed therebetween.
  • a driving shaft 59 Within the interior of a housing consisting of both housing halves 51 and 53, is rotatably secured a driving shaft 59 via a sealing means 57 and a main bearing 58, and a pin 60 is eccentrically mounted to the inner end of the driving shaft 59.
  • a counterweight 61 To a base end region of the pin 60 closer to the main bearing 58 is fixed a counterweight 61, and to the other end region is fixed a drive bush 64 which supports the movable scroll member 54 by a bearing 63 so that, in association with an anti-spin mechanism, the movable scroll member is subjected only to an orbital motion and cannot spin on its own axis. Structures and functions of the counterweight and the anti-spin mechanism are described in detail such as in Japanese Unexamined Patent Publication Nos. 57-148,087 or 57-148,092.
  • spiral bodies 522 and 542 are defined by involute curves engageable with each other, volume variations occur in each compression chamber 56 formed between the scroll members 52 and 54 in accordance with the orbital motion of the movable scroll member 54, and this causes a coolant gas to flow into the compression chamber 56 through an intake port 55, which gas is successively compressed in the chamber 56 and flows out of an exit port 65 arranged centrally in the scroll members 52, 54, into a flow-out chamber 66, and finally, is fed to a refrigeration circuit (not shown) through a fluid discharge port 67.
  • the lubrication for front side mechanisms such as the sealing means 57, the bearings 58, 63 or the anti-spin mechanism 62, is carried out by oil particles contained in the coolant gas.
  • the intake port 55 is provided in the housing wall closer to a rear side, i.e., to the compression chamber 56, rather than to the lubrication indispensable mechanisms in the front side area, so that the coolant gas can be directly taken into the compression chamber 56 while keeping the intake resistance at a lowest level. Accordingly, the coolant gas cannot be smoothly introduced to the lubrication indispensable mechanism, whereby it also becomes difficult to be sufficiently feed the lubricant in the coolant gas to such mechanisms, and in the worst case, a seizure or over-wear of these mechanisms may occur.
  • a scroll type compressor which comprises the features of the preamble of claim 1.
  • the intake port is formed in the front side area of the housing wall of the compressor housing, so that the counterweight, which is provided with vane-like projections, can positively guide the coolant gas toward lubricant indispensible mechanisms accommodated in the front side area of the interior of the compressor housing.
  • a scroll type compressor in which the intake port is formed in a region of the housing wall where the extension of the rotational plane of the counterweight intersects with the housing wall, and in which the thickness of the counterweight becomes thinner toward the periphery thereof, as a function of a distance from the rotational center of the counterweight.
  • the coolant gas is sucked into the interior of the housing through the intake port formed in the defined region of the housing wall, due to a negative pressure caused by the rotation of the counterweight.
  • the coolant gas flows into the housing without the interference of the counterweight and penetrates the lubrication indispensable mechanisms in the front side area, such as the sealing means, the main bearing or the anti-spin mechanism, whereby the sufficient lubrication can be performed. Thereafter, the coolant gas is introduced into the compression chamber.
  • a scroll type compressor of a first embodiment of the present invention has a stationary scroll member 2 consisting of a stationary side plate 21, an outer shell 22 formed integrally with the stationary side plate 21, and a stationary spiral body 23 formed in the inner side of the stationary side plate 21 and defined by an involute curve.
  • the stationary scroll member 2 is associated with a movable scroll member 4 consisting of a movable side plate 41 and a movable spiral body 42 formed in the inner side of the stationary side plate 41, and is defined by another involute curve so that a plurality of compression chambers 39 are formed by the engagement of the spiral bodies 23, 42 with each other.
  • a drive shaft 33 is rotatably supported by a sealing means 31 and a main bearing 32.
  • a pin 34 At the inner end of a larger diameter portion of the drive shaft 33 is eccentrically implanted a pin 34 to which a drive bush 36 is mounted.
  • the bush 36 rotatably supports the movable scroll member 4 through a bearing 38 so that the movable scroll member can be subjected to an orbital motion while preventing a rotation thereof about its own axis, in association with an anti-spin mechanism 37.
  • a counterweight 351 is secured to the pin 34 or the drive bush 36 for absorbing a dynamic unbalance of the movable scroll member 4.
  • the anti-spin mechanism 37 consists of a stationary race 371 fixedly secured to the front housing 30, a stationary ring 372 fixedly mounted to the race 371 and having a plurality of positioning apertures 372a circularly arranged at a distance therebetween, a plurality of balls 373, each accommodated in the respective aperture 372a, and a movable ring 374 arranged opposite to the stationary ring 372 and having a plurality of positioning apertures 374a coinciding with the respective balls 373.
  • the movable side plate 41 of the movable scroll member 4 is fixedly secured to the movable ring 374 of the anti-spin mechanism 37, and an exit port 11 is provided through the central portion of the stationary side plate 21 of the stationary scroll member 2 and communicated with the compression chamber 39 in the discharging phase.
  • a rear housing 10 is fixedly secured to the stationary scroll member 2 to form a flow-out chamber 13 inside of the rear housing 10, and the flow-out chamber 13 is communicated with the compression chamber 39 through the exit port 11 via a check valve 12, and with a refrigeration circuit through a fluid discharging port (not shown).
  • a characteristic feature of the present invention is the structure of an intake port 8 communicating with the refrigeration circuit.
  • the intake port 8 is formed in the wall of the front housing 30 so that it is positioned in a region with which an extension of a rotational plane of the counterweight 351 intersects. That is, during the rotation of the counterweight, the periphery 35a of the counterweight can alternately occupy two positions, away from the intake port 8 and closer thereto.
  • An intake path 9 is formed through the wall of the front housing 30, the stationary race 371 and the stationary ring 372 so that the intake port 8 is directly communicated with the interior of the compression chamber 39, whereby a coolant gas can flow into the compression chamber 39 without interference by the counterweight 351.
  • the compressor is driven by power from an engine (not shown) transmitted to a drive shaft 33 (Fig. 1) via an electromagnetic clutch (not shown).
  • the movable scroll member 4 is subjected to an orbital motion by the action of the driving bush 36 in association with the anti-spin mechanism 37.
  • Figure 3 illustrates the volume variation of the compression chambers 39, a shape of the counterweight 351, and a position of the intake path 9. Due to the rotation of the counterweight 351 having substantially a sector shape, a negative pressure is generated in the area behind the counterweight, when seen in the rotational direction. A coolant gas is readily introduced into the interior of the housing through the intake port 8 due to this negative pressure, and fed to the neighboring main bearing 32 and sealing means 31.
  • the coolant gas After passing through the anti-spin mechanism 37 and bearing 38, the coolant gas flows into the compression chamber 39, the interior of which has a negative pressure due to the volume variation.
  • the coolant gas In an angular phase of rotation of the counterweight 351 shown in Fig. 1, at which the periphery 35a confronts the intake port 8, the coolant gas is directly introduced into the compression chamber 39 through the intake path 9 communicating with the intake port 8. Therefore, the coolant gas can be smoothly sucked in the compression chamber 39 without interference.
  • the coolant gas in the compression chamber 39 is successively pressurized due to the orbital motion of the movable scroll member and delivered from the compression chamber 39 into the flow-out chamber 13 through the exit port 11 against the check valve 12, before being fed to the refrigeration circuit.
  • the thickness of the counterweight 351 becomes thinner as a function of a distance from the rotational center to the periphery of the counterweight, as defined by a slanted front side surface 35b.
  • the guiding of the coolant gas toward the front side is further enhanced by the slanted surface 35b when the counterweight 351 is rotating, whereby a better lubrication of the front side mechanisms is achieved.
  • the coolant gas is sufficiently fed to the lubricant indispensable mechanisms once a rotation of the counterweight.
  • the structure of the inventive compressor is relatively simple and can be easily and effectively manufactured. Also, as the intake resistance of the coolant gas is not increased compared to the conventional compressor, the engine is not subjected to an excessive burden.
  • the intake port is provided through the wall of the front housing, but this is not essential to the present invention, as the intake port may be formed in another position if the structure of the compressor permits, provided that it confronts the periphery of the counterweight. Also, the intake path need not be bored through the stationary race, if the structure of the compressor permits.

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

Claims (2)

  1. Compresseur de type spiralé comprenant un boîtier (10, 30), un élément spiralé stationnaire (2) fixé au boîtier (10), un élément spiralé mobile (4) engagé avec l'élément spiralé stationnaire (2) et formant des chambres de compression (39) entre lesdits éléments spiralés (2, 4), un arbre d'entraînement (33) monté en rotation dans le boîtier par un palier principal (32), une broche (34) montée de manière excentrique sur la région d'extrémité intérieure de l'arbre d'entraînement (33) et supportant l'élément spiralé mobile (4) de telle façon que l'élément spiralé mobile (4) est soumis à un mouvement orbital via un palier (38) tout en étant empêché, en association avec un mécanisme anti-rotation (37) de tourner autour de son propre axe, et un contrepoids (351) monté sur l'arbre d'entraînement (33) pour absorber un déséquilibre dynamique de l'élément spiralé mobile (4), le contrepoids (351) étant formé de manière à guider positivement le gaz réfrigérant vers les mécanismes (31, 33, 37, 38) pour lesquels une lubrification est indispensable qui sont logés dans la région du côté frontal à l'intérieur du boîtier de compresseur (10, 30), grâce à quoi un gaz réfrigérant est admis dans la chambre de compression (39) à travers un orifice d'admission (8) et comprimé dans la chambre de compression (39) avant d'en être déchargé suivant le mouvement orbital de l'élément spiralé mobile (4), et l'orifice d'admission (8) communique avec un trajet d'admission (9) qui est directement connecté à la chambre de compression (39), caractérisé en ce qu'une douille d'entraînement (36) est fixée sur la broche (34) et interposée entre la broche (34) et l'élément spiralé mobile (4) pour supporter celui-ci, en ce que l'orifice d'admission (8) est formé dans une région de la paroi du boîtier dans laquelle le prolongement du plan de rotation du contrepoids (351) recoupe la paroi du boîtier, et en ce que l'épaisseur du contrepoids (351) devient plus mince en direction de sa périphérie (35a), en fonction de la distance depuis le centre de rotation du contrepoids (351).
  2. Compresseur du type spiralé selon la revendication 1, caractérisé en ce que le trajet d'admission (9) est prévu au voisinage de l'orifice d'admission (8) d'une manière telle qu'il est toujours ouvert indépendamment de la phase angulaire de rotation du contrepoids (351).
EP91111968A 1990-07-18 1991-07-17 Compresseur à spirales Expired - Lifetime EP0467342B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP1990076435U JP2552309Y2 (ja) 1990-07-18 1990-07-18 スクロール型圧縮機
JP76435/90U 1990-07-18

Publications (2)

Publication Number Publication Date
EP0467342A1 EP0467342A1 (fr) 1992-01-22
EP0467342B1 true EP0467342B1 (fr) 1996-01-24

Family

ID=13605075

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91111968A Expired - Lifetime EP0467342B1 (fr) 1990-07-18 1991-07-17 Compresseur à spirales

Country Status (4)

Country Link
EP (1) EP0467342B1 (fr)
JP (1) JP2552309Y2 (fr)
KR (1) KR950007475B1 (fr)
DE (1) DE69116616T2 (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 (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5782296B2 (ja) * 2011-05-13 2015-09-24 サンデンホールディングス株式会社 スクロール型圧縮機

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5952193B2 (ja) * 1974-12-17 1984-12-18 松下電器産業株式会社 カラ−デイスプレイ装置
JPS5924992B2 (ja) * 1976-07-30 1984-06-13 大日本製薬株式会社 ピリド〔２，３−ｄ〕ピリミジン誘導体およびその製法
JPS57176382A (en) * 1981-04-24 1982-10-29 Toyoda Autom Loom Works Ltd Positive displacement fluid compressor device
JPS5924992U (ja) * 1982-08-07 1984-02-16 サンデン株式会社 スクロ−ル型圧縮機
JPS5952193U (ja) * 1982-09-30 1984-04-05 サンデン株式会社 スクロ−ル型圧縮機

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
JPH0434486U (fr) 1992-03-23
KR920002932A (ko) 1992-02-28
DE69116616D1 (de) 1996-03-07
DE69116616T2 (de) 1996-06-05
KR950007475B1 (ko) 1995-07-11
EP0467342A1 (fr) 1992-01-22
JP2552309Y2 (ja) 1997-10-29

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