[go: up one dir, main page]

EP2472114A1 - Spiralfluidmaschine - Google Patents

Spiralfluidmaschine Download PDF

Info

Publication number
EP2472114A1
EP2472114A1 EP10826303A EP10826303A EP2472114A1 EP 2472114 A1 EP2472114 A1 EP 2472114A1 EP 10826303 A EP10826303 A EP 10826303A EP 10826303 A EP10826303 A EP 10826303A EP 2472114 A1 EP2472114 A1 EP 2472114A1
Authority
EP
European Patent Office
Prior art keywords
scroll
housing
recessed portion
fluid machine
center 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Withdrawn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
EP10826303A
Other languages
English (en)
French (fr)
Other versions
EP2472114A4 (de
Inventor
Yoshihiro Ochiai
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.)
Sanden Corp
Original Assignee
Sanden Corp
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 Sanden Corp filed Critical Sanden Corp
Publication of EP2472114A1 publication Critical patent/EP2472114A1/de
Publication of EP2472114A4 publication Critical patent/EP2472114A4/de
Withdrawn legal-status Critical Current

Links

Images

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
    • 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
    • F04C23/00—Combinations of two or more pumps, each being of rotary-piston or oscillating-piston type, specially adapted for elastic fluids; Pumping installations specially adapted for elastic fluids; Multi-stage pumps specially adapted for elastic fluids
    • F04C23/008—Hermetic pumps
    • 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
    • F04C2240/52—Bearings for assemblies with supports on both sides

Definitions

  • the present invention relates to a scroll-type fluid machine, such as a scroll-type electric compressor for air-conditioning and a scroll-type expander which is loaded with an electric generator used for recovering exhaust heat from vehicles and boilers.
  • Such a compressor comprises a housing to house a pair of scroll bodies, another housing to house an electric motor and a center plate provided with mechanism component parts which convert a rotation into a swing, as disclosed in patent document 1 and 2.
  • a compressor After refrigerant is sucked from a suction port provided on a housing to house the electric motor, it passes through a void of the electric motor, and then through a void of a bearing held by the center plate or a void of an outer periphery of a cylindrical section which holds the bearing, so as to be taken into the scroll bodies and discharged from a discharge port of a housing to house the pair of scroll bodies.
  • the suction port and the discharge port are reversed so that refrigerant flows in a direction opposite to the above-described case of compressor.
  • refrigerant is sucked from a suction port provided on a housing to house a pair of scroll bodies and is taken into the scroll bodies, it passes through a void of a bearing held by the center plate or a void of an outer periphery of a cylindrical section which holds the bearing, and then through a void of the electric generator, so as to be discharged from a discharge port of a housing to house the electric generator.
  • a main shaft bearing was required to have a great load capacity without scaling up a body diameter of a compressor.
  • it is difficult to form a void as a main gas flow path because the outer diameter of a cylindrical section holding the bearing becomes almost equal to the inner diameter of a coupling section of a movable scroll body when the outer diameter of the bearing is enlarged in order to increase the load capacity of the bearing without changing the inner diameter which may affect on another component part.
  • performance deterioration from pressure loss during high flow-rate operation is prevented only by the void of the bearing.
  • an object of the present invention is to provide a scroll-type fluid machine which can achieve a long life and a reduction in size and weight while a bearing with greater load capacity is incorporated without enlarging the body diameter and which can prevent the performance deterioration from pressure loss during high flow-rate operation by ensuring the section area of the gas flow path of the center plate.
  • a scroll-type fluid machine is a scroll-type fluid machine comprising a first housing which houses a scroll mechanism made of a fixed scroll and a movable scroll, a second housing which houses an electric motor to rotate a main shaft, and a center plate, which is interposed between the housings, which has a motion conversion mechanism to convert a rotation motion of the main shaft to a swing motion of the movable scroll, which is provided with a rotation preventing mechanism for the movable scroll, and which holds a bearing to hold the main shaft, and a fluid path which communicates an inside of the second housing and an inside of the first housing through an installation part of the center plate, characterized in that at least a part of the fluid path is formed by connecting an axial recessed portion and a radial recessed portion, which are formed in the center plate, the axial recessed portion facing the inside of the second housing and extending in an axial direction, the radial recessed portion being located closer to the first housing than the bearing and
  • At least a part of the fluid path which connects the inside of the first housing and the inside of the second housing through the center plate, is formed by connecting the axial recessed portion and the radial recessed portion which are formed in the center plate, so as to sufficiently ensure the section area of the gas flow path and to prevent the performance from deteriorating by pressure loss during a high flow-rate operation.
  • the fluid path is formed by connecting the axial recessed portion extending axially along the main shaft and the radial recessed portion extending radially, so that the gas flow path can be formed by a simple processing.
  • a plurality of the axial recessed portions are formed along a circumferential direction.
  • Such axial recessed portions make it easy to ensure the section area of the fluid path even if a bearing with relatively high load capacity is incorporated.
  • a part of an inner surface of the axial recessed portion is formed to be a surface extending in a shape tapered toward the inside of the second housing.
  • the axial recessed portion is formed in such a shape, so that the strength of the center plate is maintained and the processing is simplified.
  • the radial recessed portion is formed to be a ring-shaped recess extending in a circumferential direction.
  • the radial recessed portion is formed in such a shape, so that the processing is simplified.
  • a part of an inner surface of the radial recessed portion is formed to be a surface extending in a shape tapered toward the inside of the second housing from the inside of the first housing.
  • the radial recessed portion is formed in such a shape, so that the strength of the center plate is maintained and the processing is simplified.
  • the axial recessed portion is provided at a time of producing a material for the center plate.
  • the axial recessed portion is provided at the same time of producing the material for the center plate, so that the production process of the center plate can be simplified.
  • the material for the center plate is produced by casting and the axial recessed portion is formed with a die.
  • the radial recessed portion is formed with a core mold. Such a production process is employed, so that the center plate can be produced further efficiently.
  • the radial recessed portion is formed by machining.
  • the machining can be easily performed especially in a case where the radial recessed portion is formed into a ring-shaped recess extending in a circumferential direction.
  • the center plate is formed integrally with either the first housing or the second housing.
  • the center plate is formed to be unified with the first housing or the second housing, the number of component parts can be reduced and the assembly process of the scroll-type fluid machine can be simplified.
  • the scroll-type fluid machine of the present invention can be constructed as a compressor or an expander. Namely, in the scroll-type fluid machine of the present invention, function as a compressor or an expander can be shown as depending on the rotational direction of the main shaft. Specifically when it is constructed as a compressor, it is preferable that a discharge valve is provided.
  • the scroll-type fluid machine according to the present invention is suitably used as a fluid machine loaded in a vehicle. Because fluid machines loaded in vehicles are strongly required to have a small size and a light weight, technical features of the scroll-type fluid machine of the present invention can be brought out effectively therein.
  • a scroll-type fluid machine makes it possible that the section area of the fluid path is sufficiently ensured by a simple processing and that the performance deterioration caused by a pressure loss during high flow-rate operation is efficiently prevented. As a result, it is not necessary for the body diameter to enlarge even when a bearing having higher load capacity is incorporated, so that a small-sized and light-weight fluid machine is achieved with a long life.
  • the section area of the fluid path of the center plate is sufficiently ensured, so that the performance deterioration caused by a pressure loss in a high flow-rate operation is prevented.
  • Fig. 1 is a longitudinal section view of a scroll-type compressor according to an embodiment of the present invention.
  • Compressor 1 comprises first housing 4 to house fixed scroll 2 and movable scroll 3, crank mechanism 6 to convert the rotation of main shaft 5 to the swing of movable scroll 3, center plate 8 provided with rotation preventing mechanism 7 to prevent movable scroll 3 from rotating and second housing 10 to house electric motor 9, wherein electric motor 9 and compressor 1 are disposed in the same axis.
  • Cylindrical bearing holding section 12 to hold bearing 11 of main shaft 5 is attached to a surface at electric motor 9 side of center plate 8.
  • a plurality of radially formed ribs (not shown) are provided at the outer side from bearing holding section 12 in a radial direction.
  • a plurality of radial recessed portions 13 extending axially along main shaft 5 are formed to have inner surfaces which extend as tapering toward the inside of second housing 10.
  • a surface of first housing 4 side of center plate 8 is provided with radial recessed portion 14 which extends in a direction perpendicular to main shaft 5 and which is formed to be a ring-shaped recess extending over a whole circumference of center plate 8.
  • the inner surface of radial recessed portion 14 is formed in a tapered shape extending in parallel with main shaft 5 from the inside of first housing 4 toward the inside of second housing 10 (electric motor 9 side).
  • the refrigerant gas sucked from suction port 15 is delivered through a gap of electric motor 9 to a front side of center plate 8, and then, is taken into movable scroll 3 mainly via axial recessed portion 13 and radial recessed portion 14. After it is compressed by a compression mechanism made of movable scroll 3 and fixed scroll 2, it is discharged from discharge port 18 via discharge hole 16 and discharge chamber 17.
  • the refrigeration circuit of compressor 1 is constructed to make such a path.
  • refrigerant gas which conventionally used to flow in a gap of bearing 11 or a gap at the outer periphery side of bearing holding section 12, comes to be able to flow inside a fluid path made of the radial recessed portion 14 and axial recessed portion 13 so as to ensure the section area of the refrigerant gas flow path, the pressure loss can be reduced in a high flow-rate operation.
  • Fig. 2 is a partial enlarged longitudinal section view where a neighborhood of part A of Fig. 1 has been enlarged. Desirable size and shape of axial recessed portion 13 and radial recessed portion 14 will be explained as referring to Fig. 2 as follows.
  • axial length a in an overlap region of axial recessed portion 13 and radial recessed portion 14 is 2-9 mm.
  • excessively long length a would weaken the strength of center plate 9.
  • angle b which is wedged between an end surface at movable scroll 3 side of center plate 9 and a tapered inner surface of radial recessed portion 14, is 20-60 degrees. Angle b within this range makes it easy to process radial recessed portion 14.
  • angle c (e) between the tapered inner surface of axial recessed portion 13 and the axial direction is 1-4 degrees. Angle c within this range makes it possible to improve fluidity of refrigerant gas which flows into axial recessed portion 13 from the inside of second housing 10 as well as to simplify processing radial recessed portion 14.
  • radial depth d of radial recessed portion 14 is 3-9mm. Depth d within this range makes it possible to improve fluidity of refrigerant gas which flows from axial recessed portion 13 via radial recessed portion 14 into the inside of first housing 4 as well as to simplify processing radial recessed portion 14.
  • a scroll-type fluid machine according to the present invention is suitably used as a compressor for vehicles, etc., which is required to have a small side and light weight.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP10826303.9A 2009-10-26 2010-10-21 Spiralfluidmaschine Withdrawn EP2472114A4 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2009245752A JP2011089507A (ja) 2009-10-26 2009-10-26 スクロール型流体機械
PCT/JP2010/006250 WO2011052166A1 (ja) 2009-10-26 2010-10-21 スクロール型流体機械

Publications (2)

Publication Number Publication Date
EP2472114A1 true EP2472114A1 (de) 2012-07-04
EP2472114A4 EP2472114A4 (de) 2013-08-21

Family

ID=43921602

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10826303.9A Withdrawn EP2472114A4 (de) 2009-10-26 2010-10-21 Spiralfluidmaschine

Country Status (7)

Country Link
US (1) US20120237374A1 (de)
EP (1) EP2472114A4 (de)
JP (1) JP2011089507A (de)
KR (1) KR20120049369A (de)
CN (1) CN102575671A (de)
CA (1) CA2775384A1 (de)
WO (1) WO2011052166A1 (de)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP5648566B2 (ja) 2011-04-13 2015-01-07 スズキ株式会社 腐食環境センサおよび腐食環境測定方法
EP3744980B1 (de) * 2018-01-25 2023-11-29 Toshiba Carrier Corporation Drehkompressor und kühlkreisvorrichtung
JP6943215B2 (ja) 2018-03-30 2021-09-29 株式会社豊田自動織機 電動圧縮機

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5447415A (en) * 1992-06-29 1995-09-05 Sanden Corporation Motor driven fluid compressor within hermetic housing
JPH08105392A (ja) * 1994-10-05 1996-04-23 Mitsubishi Heavy Ind Ltd スクロール型圧縮機
US20020071778A1 (en) * 2000-12-08 2002-06-13 Eiji Kobayashi Scroll-Type Compressors
JP2005307949A (ja) * 2004-04-26 2005-11-04 Sanden Corp スクロール型流体機械
JP2006105064A (ja) * 2004-10-07 2006-04-20 Sanden Corp 圧縮機
US20070269327A1 (en) * 2006-05-22 2007-11-22 Nanjing Aotecar Refrigerating Compressor Co., Ltd. Constant Pressure Type and Fully Enclosed Scroll Compressor for Vehicle
EP1970568A1 (de) * 2006-01-05 2008-09-17 Sanden Corporation Elektrischer verdichter
EP1980749A1 (de) * 2006-01-30 2008-10-15 Sanden Corporation Elektrischer kompressor und klimaanlagensystem mit dem elektrischen kompressor für ein fahrzeug
WO2009096288A1 (ja) * 2008-01-29 2009-08-06 Mitsubishi Heavy Industries, Ltd. 密閉型スクロール圧縮機

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6248988A (ja) * 1985-08-16 1987-03-03 Hitachi Ltd 密閉形スクロ−ル圧縮機
JPS62203992A (ja) * 1986-03-03 1987-09-08 Hitachi Ltd 密閉形スクロ−ル圧縮機
JP2002070762A (ja) * 2000-08-29 2002-03-08 Toyota Industries Corp 燃料電池用スクロール型圧縮機
JP2002257063A (ja) * 2001-02-28 2002-09-11 Sanden Corp スクロール型圧縮機
JP3933492B2 (ja) * 2002-02-19 2007-06-20 サンデン株式会社 スクロール型圧縮機
JP2003343458A (ja) * 2002-05-23 2003-12-03 Mitsubishi Heavy Ind Ltd スクロール型圧縮機
US20080101974A1 (en) * 2006-11-01 2008-05-01 Samsung Electronics Co., Ltd. Rotary compressor
JP2008232057A (ja) 2007-03-22 2008-10-02 Sanden Corp オイルセパレータ内蔵圧縮機
JP2008303819A (ja) 2007-06-08 2008-12-18 Sanden Corp スクロール圧縮機

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5447415A (en) * 1992-06-29 1995-09-05 Sanden Corporation Motor driven fluid compressor within hermetic housing
JPH08105392A (ja) * 1994-10-05 1996-04-23 Mitsubishi Heavy Ind Ltd スクロール型圧縮機
US20020071778A1 (en) * 2000-12-08 2002-06-13 Eiji Kobayashi Scroll-Type Compressors
JP2005307949A (ja) * 2004-04-26 2005-11-04 Sanden Corp スクロール型流体機械
JP2006105064A (ja) * 2004-10-07 2006-04-20 Sanden Corp 圧縮機
EP1970568A1 (de) * 2006-01-05 2008-09-17 Sanden Corporation Elektrischer verdichter
EP1980749A1 (de) * 2006-01-30 2008-10-15 Sanden Corporation Elektrischer kompressor und klimaanlagensystem mit dem elektrischen kompressor für ein fahrzeug
US20070269327A1 (en) * 2006-05-22 2007-11-22 Nanjing Aotecar Refrigerating Compressor Co., Ltd. Constant Pressure Type and Fully Enclosed Scroll Compressor for Vehicle
WO2009096288A1 (ja) * 2008-01-29 2009-08-06 Mitsubishi Heavy Industries, Ltd. 密閉型スクロール圧縮機

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See also references of WO2011052166A1 *

Also Published As

Publication number Publication date
US20120237374A1 (en) 2012-09-20
EP2472114A4 (de) 2013-08-21
CN102575671A (zh) 2012-07-11
KR20120049369A (ko) 2012-05-16
CA2775384A1 (en) 2011-05-05
JP2011089507A (ja) 2011-05-06
WO2011052166A1 (ja) 2011-05-05

Similar Documents

Publication Publication Date Title
EP2589808A1 (de) Spiralverdichter
EP2541063B1 (de) Verfahren zur montage eines elektrischen kompressors
CN109563833B (zh) 双旋转涡旋型压缩机及其设计方法
WO2011016452A1 (ja) 圧縮機
US20040105770A1 (en) Scroll fluid machine
US7641454B2 (en) Two-stage rotary compressor
US8535029B2 (en) Scroll type compressor having reinforced fixed scroll
EP2472114A1 (de) Spiralfluidmaschine
EP1850006B1 (de) Spiralverdichter
JP4884904B2 (ja) 流体機械
CN102312836B (zh) 多气缸旋转式压缩机、其组装方法以及其制造装置
JP2006183527A (ja) 流体機械
EP3051131B1 (de) Verdichter und verfahren zur herstellung des verdichters
JP3858762B2 (ja) スライドブッシュ及びスクロール型流体機械
JP2005188393A (ja) 電動ポンプ
JP4556183B2 (ja) スクロール流体機械
CN110214230B (zh) 涡旋式压缩机
JP4051121B2 (ja) 密閉形圧縮機
JP6004633B2 (ja) スクロール型圧縮機
KR101376613B1 (ko) 크랭크축 및 이를 구비한 압축기
EP3677784B1 (de) Drehwelle eines drehverdichters und drehverdichter
JP6810658B2 (ja) スクロール圧縮機
JP4350603B2 (ja) 気体圧縮機
EP2918773B1 (de) Rotationsverdichter
US12209583B2 (en) Scroll compressor

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20120326

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

DAX Request for extension of the european patent (deleted)
A4 Supplementary search report drawn up and despatched

Effective date: 20130722

RIC1 Information provided on ipc code assigned before grant

Ipc: F04C 23/00 20060101ALI20130716BHEP

Ipc: F04C 18/02 20060101AFI20130716BHEP

17Q First examination report despatched

Effective date: 20140730

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION IS DEEMED TO BE WITHDRAWN

18D Application deemed to be withdrawn

Effective date: 20141210