EP3109475A1 - Machine à fluides à volute - Google Patents

Machine à fluides à volute Download PDF

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Publication number
EP3109475A1
EP3109475A1 EP14883157.1A EP14883157A EP3109475A1 EP 3109475 A1 EP3109475 A1 EP 3109475A1 EP 14883157 A EP14883157 A EP 14883157A EP 3109475 A1 EP3109475 A1 EP 3109475A1
Authority
EP
European Patent Office
Prior art keywords
back face
face plate
scroll
orbiting scroll
driving shaft
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.)
Granted
Application number
EP14883157.1A
Other languages
German (de)
English (en)
Other versions
EP3109475B1 (fr
EP3109475A4 (fr
Inventor
Yoshio Kobayashi
Toshikazu Harashima
Kiminori Iwano
Kazutaka Suefuji
Sho Watanabe
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.)
Hitachi Industrial Equipment Systems Co Ltd
Original Assignee
Hitachi Industrial Equipment Systems Co 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 Hitachi Industrial Equipment Systems Co Ltd filed Critical Hitachi Industrial Equipment Systems Co Ltd
Publication of EP3109475A1 publication Critical patent/EP3109475A1/fr
Publication of EP3109475A4 publication Critical patent/EP3109475A4/fr
Application granted granted Critical
Publication of EP3109475B1 publication Critical patent/EP3109475B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01C—ROTARY-PISTON OR OSCILLATING-PISTON MACHINES OR ENGINES
    • F01C17/00—Arrangements for drive of co-operating members, e.g. for rotary piston and casing
    • F01C17/06—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements
    • F01C17/063—Arrangements for drive of co-operating members, e.g. for rotary piston and casing using cranks, universal joints or similar elements with only rolling movement
    • 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
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • 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
    • F04C2240/30—Casings or housings
    • 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
    • F04C2240/60—Shafts
    • 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
    • F04C2240/80—Other components
    • F04C2240/805—Fastening means, e.g. bolts

Definitions

  • the present invention relates to a scroll type fluid machine.
  • Patent Literature 1 discloses "a cooling structure in a scroll fluid machine characterized in that at least a back face of a boss portion for an auxiliary crank and a center portion corresponding to a boss portion for the rotating shaft are brought into contact with a cooling fin tip portion on the orbiting scroll side and are integrated with the orbiting scroll".
  • Patent Literature 1 Japanese Patent No. 4130285
  • the present invention provides a scroll type fluid machine including a fixed scroll, an orbiting scroll provided to be opposed to the fixed scroll and moved to orbit, a casing provided on an outer side of the orbiting scroll, a driving shaft for driving the orbiting scroll, a back face plate fastened to the orbiting scroll and connected to the driving shaft by a boss portion, and a rotation preventing mechanism provided between the casing and the back face plate for preventing a rotation of the orbiting scroll, in which the back face plate includes a rotation preventing mechanism side back face plate integrally provided with the rotation preventing mechanism and a driving shaft side back face plate provided integrally with the boss portion, and the rotation preventing mechanism side back face plate is not in contact with the orbiting scroll.
  • a scroll type fluid machine realizing the reliability improvement and the long life of a rotation preventing mechanism can be provided.
  • FIG. 1 shows the sectional view of the scroll type compressor according to the present embodiment.
  • a casing 1 of the scroll type air compressor is formed in a cylindrical shape, provided on an outer side of an orbiting scroll 8, and rotatably supports a driving shaft 15 at inside thereof.
  • a fixed scroll 2 provided on an opening side of the casing 1 is substantially configured by an end plate 3 formed substantially in a circular plate shape centering on an axial line O-O, a lap portion 4 in a scroll shape erected in an axial direction at a tooth bottom face which become a surface of the end plate 3, an outer peripheral wall portion 5 in a cylindrical shape provided on an outer diameter side of the end plate 3 by surrounding the lap portion 4, and plural cooling fins 6 projected from a back face of the end plate 3 as shown in Fig. 1 .
  • the lap portion 4 is wound in a scroll shape of, for example, around three windings from an inner diameter side to an outer diameter side when, for example, the innermost diameter end is made to be a winding start end and the outermost diameter end is made to be a winding finish end. Further, the tooth tip face of the lap portion 4 is separated from the tooth bottom face of the end plate 9 of the orbiting scroll 8 which becomes a counterpart by a constant axial direction dimension.
  • the tooth tip face of the lap portion 4 is provided with a seal groove 4A along a winding direction of the lap portion 4, and a tip seal 7 as a seal member which is brought into abrasive contact with the end plate 9 of the orbiting scroll 8 is provided in the seal groove 4A.
  • the outer peripheral wall portion 5 is opened to an end face of the fixed scroll 2 by substantially configuring a circular shape. Further, the outer peripheral wall portion 5 is arranged on an outer side in a diameter direction of the lap portion 10 to avoid an interference with the lap portion 10 of the orbiting scroll 8.
  • the orbiting scroll 8 provided to be able to orbit in the casing 1 is substantially configured by an end plate 9 substantially in a circular plate shape arranged opposedly to the end plate 3 of the fixed scroll 2, the lap portion 10 in a scroll shape erected from the tooth bottom face which becomes a surface of the end plate 9, and plural cooling fins 11 projected from a back face of the end plate 9.
  • a back face plate 12 connected to a driving shaft 15 is provided on a tip end side of the cooling fin 11.
  • the lap portion 10 configures a scroll shape of, for example, around 3 windings substantially similar to the lap portion 4 of the fixed scroll 2. Further, a tooth tip face of the lap portion 10 is separated by a constant axial direction dimension from a tooth bottom face of the end plate 3 of the fixed scroll 2 which becomes a counterpart. Further, the tooth tip face of the lap portion 10 is provided with a seal groove 10A along a winding direction of the lap portion 10, and a tip seal 13 as a seal member which is brought into abrasive contact with the end plate 3 of the fixed scroll 2 is provided in the seal groove 10A.
  • a boss portion 14 in a cylindrical shape connected to a crank portion 15A of the driving shaft 15 is integrally formed with a center side of the back face plate 12 via an orbiting bearing 14a and a bearing housing 14b.
  • a pulley 15B is provided to be disposed at an outer portion of the casing 1 on one end side of the driving shaft 15, the pulley 15B is connected to an output side of an electric motor as, for example, the driving source via a belt (both not illustrated) or the like.
  • the driving shaft 15 is rotationally driven by the electric motor or the like and moves to orbit the orbiting scroll 8 relative to the fixed scroll 2.
  • the pulley 15B is attached with a cooling fan 16 by using a bolt or the like, and the cooling fan 16 generates cooling wind in a fan casing 17.
  • the cooling fan 16 sends cooling wind to an inner portion of the casing 1 and back face sides of the respective scrolls 2 and 8 along a duct or the like in the fan casing 17, and cools the casing 1, the fixed scroll 2, the orbiting scroll 8 and the like.
  • auxiliary cranks 18 as, for example, three rotation preventing mechanisms (only one is illustrated) for preventing rotation of the orbiting scroll 8 are provided between the back face plate 12 and the casing 1.
  • the auxiliary cranks 18 are arranged in auxiliary crank boss portions 18b respectively formed at the casing 1 and the back face plate 12 via auxiliary crank bearings.
  • Plural compression chambers 19 provided between the fixed scroll 2 and the orbiting scroll 8 are successively formed from an outer side in a diameter direction over to an inner side in the diameter direction to be disposed between the lap portions 4 and 10, and maintained in airtight by the tip seals 7 and 13. Further, when the orbiting scroll 8 is moved to orbit in a forward direction, the respective compression chambers 19 are continuously reduced therebetween while moving from outer sides in a diameter direction to inner sides in the diameter direction of the lap portions 4 and 10.
  • outside air is sucked from a suction port 20 to be described later to a compression chamber 19A disposed on an outer side in a diameter direction in the respective compression chambers 19.
  • the air is compressed to be compressed air before it reaches a compression chamber 19B disposed on an inner side in a diameter direction.
  • the compressed air is delivered from a delivery port 22 and stored at an outside storing tank (not illustrated).
  • the suction port 20 provided on the outer diameter side of the fixed scroll 2 is opened from an outer diameter side over to the outer peripheral wall portion 5 of the end plate 3, and communicates with the compression chamber 19A disposed on an outer side in a diameter direction. Further, the suction port 20 is disposed on an outer side in a diameter direction of the lap portion 10 of the orbiting scroll 8 in the end plate 3 of the fixed scroll 2, is opened to a range where the tip seal 13 is not brought into abrasive contact (nonabrasive area) . Further, the suction port 20 sucks, for example, air at the atmospheric pressure into the compression chamber 19A disposed on an outer side in a diameter direction through a suction filter 21.
  • the suction port 20 may be configured to suck compressed air.
  • the suction port 20 may be configured to connect the suction port 20 to a piping supplied with compressed air by removing the suction filter 21.
  • a flange 24 disposed on an outer side in a diameter direction of the lap portion 4 of the fixed scroll 2 fixes the fixed scroll 2 to the casing 1 by a flange 1a of the casing 1.
  • Positioning of the fixed scroll 2 and the casing 1 is carried out by inserting a positioning member by a positioning hole 37.
  • a face seal groove 25 provided at an end face of the fixed scroll 2 opposed to the end plate 9 of the orbiting scroll 8 is disposed on an outer side in a diameter direction of the outer peripheral wall portion 5 and formed in a shape of a circular ring surrounding the outer peripheral wall portion 5. Further, a face seal 26 in the circular ring shape is attached into the face seal groove 25. Further, the face seal 26 seals an interval between an end face of the fixed scroll 2 and the end plate 9 of the orbiting scroll 8 in airtight and prevents air sucked into the outer peripheral wall portion from therebetween from leaking.
  • the scroll type air compressor according to the present embodiment is configured as described above, and next, a description will be given of an operation of the scroll type air compressor.
  • the orbiting scroll 8 carries out an orbiting movement centering on an axial direction O-O of the driving shaft 15 in a state of preventing rotation by the rotation preventing mechanism, and the compression chamber 19 partitioned between the lap portion 4 of the fixed scroll 2 and the lap portion 10 of the orbiting scroll 2 is continuously reduced.
  • air sucked from the suction port 20 of the fixed scroll 2 can be delivered from the delivery port 22 of the fixed scroll 2 to an outside tank (not illustrated) as compressed air while being compressed successively by the respective compression chambers 19.
  • Cooling wind generated by the cooling fan 16 flows to an inner portion of the casing 1 and the back face sides of the respective scrolls 2 and 8 along a duct or the like in the fan casing 17, and cools the casing 1, the fixed scroll 2, the orbiting scroll 8 and the like.
  • Fig. 2 shows the back face of the orbiting scroll 8 according to the present embodiment.
  • the orbiting scroll 8 is formed with the cooling fin 11 on the back face side of the end plate 9. Further, plural fastening portions 38 fastened to the back face plate 12 are provided at the back face of the scroll 8.
  • the cooling fin 11 and the fastening portion 38 may be integrally formed. Thereby, the flow of the cooling wind between the cooling fins 11 is not hampered by the fastening portion 38, and therefore, the orbiting scroll 8 and the back face plate 11 can be fastened without reducing cooling efficiency of the orbiting scroll 8 and the back face plate 12.
  • cooling fin may be provided to not only the orbiting scroll 8 but the back face plate 12. Thereby, a temperature rise of the back face plate can further be restrained.
  • Fig. 3 shows the back face plate 12 fastened to the orbiting scroll 8.
  • the back face plate 12 is configured by a driving shaft side back face plate 12a integrally formed with the boss portion 14 connected to the driving shaft 15, and a rotation preventing mechanism side back face plate 12b integrally formed with the auxiliary crank bearing housing 18b accommodating the plural auxiliary cranks 18.
  • a hollow portion 39 is provided between the driving shaft side back face plate 12a and the rotation preventing mechanism side back face plate 12b as well as the driving shaft side back face plate 12a and the rotation preventing mechanism side back face plate 12b are not connected in a diameter direction.
  • the rotation preventing mechanism side back face plate 12b is connected to the driving shaft side back face plate 12a in a peripheral direction via a connecting portion 13.
  • the thermal deformation can be absorbed by the hollow portion 39. Therefore, the thermal expansion of the driving shaft side back face plate 12a is not transferred to the rotation preventing mechanism side back face plate 12b, and a strain of the auxiliary crank bearing housing 18b can be restrained.
  • the driving shaft side back face plate 12a may be formed by a material having rigidity lower than that of the rotation preventing mechanism side back face plate 12b. Thereby, more of deformation by the thermal expansion can be absorbed by the driving shaft side back face plate 12a, the strain of the auxiliary crank bearing housing 18b can be restrained more effectively, and the reliability and the life of the auxiliary crank can be improved further.
  • Fig. 4 shows the orbiting scroll 8 fastened with the back face plate 12.
  • the present embodiment is configured such that the cooling fin 11 formed on the back face side of the orbiting scroll 8 is not in contact with the rotation preventing mechanism side back face plate 12b in a state where the orbiting scroll 8 and the back face plate 12 are fastened by the fastening portion 38.
  • a dimension in an axial direction (longitudinal direction of the driving shaft 15) of the cooling fin 11 is formed to be larger than that at a position opposed to the rotation preventing mechanism back face plate 12b, and the cooling fin 11 is configured to be brought into contact with the driving shaft side back face plate 12a.
  • the cooling fin 11 is configured to be brought into contact with the driving shaft side back face plate 12a, and therefore allowing the heat of the orbiting scroll 8 to escape effectively. Even when configured in this way, the driving side back face plate 12a and the rotation preventing mechanism side back face plate 12b are not in contact in a diameter direction, and therefore, the heat transfer to the rotation preventing mechanism side back face plate 12b is not increased. Further, the heat transfer to the rotation preventing mechanism side back face plate 12b can be restrained further by preventing the contact with the cooling fin 11 at the connecting portion 13.
  • the cooling wind flowing into a space formed between the orbiting scroll 8 and the back face plate 12 flows, and therefore, the temperature rise of the rotation preventing mechanism side back face plate 12b and the auxiliary crank 18 can be restrained while allowing the heat of the orbiting scroll 8 to escape effectively.
  • the temperature rise of the rotation preventing mechanism side back face plate 12b and the auxiliary crank 18 can be restrained while allowing the heat of the orbiting scroll 8 to escape effectively. Further, temperature reduction of the auxiliary crank 18 can be carried out without adding parts, the cost can be reduced, and also a number of working steps (working time) can be reduced since mechanical working portions are reduced.
  • the present invention is not limited thereto, and the present invention may be applied to other scroll type fluid machine of a coolant compressor of compressing a coolant, a vacuum pump and the like. Further, the present invention may be applied to a system of a tank integrated type package compressor or a nitrogen gas generating apparatus having a scroll type fluid machine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP14883157.1A 2014-02-21 2014-02-21 Machine à fluide de type à volute Active EP3109475B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2014/054101 WO2015125261A1 (fr) 2014-02-21 2014-02-21 Machine à fluides à volute

Publications (3)

Publication Number Publication Date
EP3109475A1 true EP3109475A1 (fr) 2016-12-28
EP3109475A4 EP3109475A4 (fr) 2018-01-24
EP3109475B1 EP3109475B1 (fr) 2019-08-07

Family

ID=53877795

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14883157.1A Active EP3109475B1 (fr) 2014-02-21 2014-02-21 Machine à fluide de type à volute

Country Status (5)

Country Link
EP (1) EP3109475B1 (fr)
JP (1) JP6205478B2 (fr)
KR (1) KR101886668B1 (fr)
CN (1) CN105849411B (fr)
WO (1) WO2015125261A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3239531A1 (fr) * 2016-04-25 2017-11-01 Zhejiang Jieneng Compression Equipment Co., Ltd. Ensemble de dissipation de chaleur de disque de défilement de compresseurs à spirales

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113217376A (zh) * 2021-05-28 2021-08-06 浙江蓝德华燕动力有限公司 一种高抽速无油涡旋真空泵

Family Cites Families (17)

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Publication number Priority date Publication date Assignee Title
US5466134A (en) * 1994-04-05 1995-11-14 Puritan Bennett Corporation Scroll compressor having idler cranks and strengthening and heat dissipating ribs
JP3645339B2 (ja) * 1995-11-20 2005-05-11 株式会社日立製作所 スクロール式流体機械
JP4130285B2 (ja) 1999-10-29 2008-08-06 アネスト岩田株式会社 スクロール流体機械における冷却構造
JP4028179B2 (ja) * 2001-03-06 2007-12-26 アネスト岩田株式会社 スクロール流体機械
JP2003065267A (ja) * 2001-08-30 2003-03-05 Hokuetsu Kogyo Co Ltd オイルフリー・スクロール流体機械
JP2003065271A (ja) * 2001-08-30 2003-03-05 Hokuetsu Kogyo Co Ltd オイルフリー・スクロール流体機械
JP2005282495A (ja) * 2004-03-30 2005-10-13 Anest Iwata Corp スクロール流体機械
JP4494885B2 (ja) 2004-06-30 2010-06-30 株式会社日立製作所 スクロール式流体機械
JP5020628B2 (ja) * 2006-12-26 2012-09-05 アネスト岩田株式会社 スクロール流体機械
JP2008185020A (ja) 2007-01-31 2008-08-14 Hitachi Ltd スクロール式流体機械
JP2010084592A (ja) * 2008-09-30 2010-04-15 Hitachi Ltd スクロール式流体機械
JP5286108B2 (ja) * 2009-03-02 2013-09-11 株式会社日立産機システム スクロール式流体機械
JP5457943B2 (ja) * 2010-06-02 2014-04-02 株式会社日立産機システム スクロール式流体機械
JP5422609B2 (ja) * 2011-06-10 2014-02-19 株式会社日立産機システム スクロール式流体機械
CN103291616A (zh) * 2012-03-02 2013-09-11 日本株式会社富石 涡旋式流体机械
CN103089619A (zh) * 2012-11-14 2013-05-08 柳州易舟汽车空调有限公司 涡旋压缩机
JP2018005020A (ja) * 2016-07-05 2018-01-11 凸版印刷株式会社 カラーフィルタ及びその製造方法

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3239531A1 (fr) * 2016-04-25 2017-11-01 Zhejiang Jieneng Compression Equipment Co., Ltd. Ensemble de dissipation de chaleur de disque de défilement de compresseurs à spirales

Also Published As

Publication number Publication date
EP3109475B1 (fr) 2019-08-07
KR20160070135A (ko) 2016-06-17
JP6205478B2 (ja) 2017-09-27
JPWO2015125261A1 (ja) 2017-03-30
KR101886668B1 (ko) 2018-08-09
EP3109475A4 (fr) 2018-01-24
CN105849411A (zh) 2016-08-10
CN105849411B (zh) 2019-03-08
WO2015125261A1 (fr) 2015-08-27

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