EP0070617A2 - Einrichtung vom Spiraltyp zum Fördern von Fluid - Google Patents

Einrichtung vom Spiraltyp zum Fördern von Fluid Download PDF

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Publication number
EP0070617A2
EP0070617A2 EP82302818A EP82302818A EP0070617A2 EP 0070617 A2 EP0070617 A2 EP 0070617A2 EP 82302818 A EP82302818 A EP 82302818A EP 82302818 A EP82302818 A EP 82302818A EP 0070617 A2 EP0070617 A2 EP 0070617A2
Authority
EP
European Patent Office
Prior art keywords
end plate
housing
scroll
fluid displacement
opening portion
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
EP82302818A
Other languages
English (en)
French (fr)
Other versions
EP0070617A3 (en
EP0070617B1 (de
Inventor
Masaharu Hiraga
Kazuo Sugimoto
Tadashi Sato
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 EP0070617A2 publication Critical patent/EP0070617A2/de
Publication of EP0070617A3 publication Critical patent/EP0070617A3/en
Application granted granted Critical
Publication of EP0070617B1 publication Critical patent/EP0070617B1/de
Expired 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
    • F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
    • F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
    • F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
    • 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
    • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/24—Control of, monitoring of, or safety arrangements for, machines or engines characterised by using valves for controlling pressure or flow rate, e.g. discharge valves
    • F01C20/26—Control of, monitoring of, or safety arrangements for, machines or engines characterised by using valves for controlling pressure or flow rate, e.g. discharge valves using bypass channels
    • F01C20/265—Control of, monitoring of, or safety arrangements for, machines or engines characterised by using valves for controlling pressure or flow rate, e.g. discharge valves using bypass channels being obtained by displacing a lateral sealing face

Definitions

  • This invention relates to a fluid displacement apparatus, and more particularly, to a scroll type fluid displacement apparatus for use as a supercharger for a engine or as an air pump.
  • Scroll type fluid displacement apparatus are well known in the prior art.
  • U.S.Patent No. 801,182 discloses a device including two scrolls each having a circular end plate and a spiroidal or involute spiral element. These scrolls are maintained angularly and radially offset so that both spiral elements interfit to make 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 scrolls shifts the line contacts along the spiral curved surfaces and, as a result, the volume of the fluid pockets changes.Since, the volume of the fluid pockets increases or decreases dependent on the direction of the orbital motion, the scroll type fluid displacement apparatus is applicable to compress, expand or pump fluids.
  • Scroll type fluid displacement apparatus have been used as a refrigerant compressor in refrigerator or air conditioning apparatus.
  • Such compressors need high efficiency and a high compression ratio, such as 5 to 10 compression ratio.
  • the re-expansion volume i.e., the smallest volume of the fluid pockets in a compression cycle, which is located at the center of the scroll members in a scroll type compressor, must be reduced as much as possible.
  • the inner end portion of the spiral elements are extended inwardly as far as possible to the center of the scroll member..
  • The_engine with the supercharger is controlled by external environment, for example, in starting or high power driving situation, the engine needs the supercharged air to power up the engine, while, in the constant drive situation, the engine requiring not so much supercharged air.
  • the supercharger must be provided with the control means for the operation of the apparatus.
  • a scroll type fluid displacement apparatus includes a housing having a fluid inlet port and a fluid outlet port.
  • Fixed scroll member is joined- with the housing and has a first end plate from which a first wrap extends into an operative interior area of the housing.
  • An orbiting scroll member has a second end plate from which a second wrap extends. The first and second wraps interfit at an angular and radial offset to make a plurality of line contacts to define at least one pair of fluid pockets.
  • a driving mechanism is connected to the orbiting scroll to drive the orbiting scroll in an orbital motion.
  • a rotation preventing device is disposed between the housing and the second end plate for preventing the rotation of the orbiting scroll, thereby the volume of the fluid pockets changes by the orbital motion of the scroll.
  • An opening is formed through the first end plate for connecting between the lower pressure space within the operative area of the housing and a center space of wraps.
  • a control means is disposed in the opening for controlling the opening and closing of the opening.
  • Apparatus 1 includes a housing 10 having a front end plate 11 and a cup shaped casing 12, which is attached to one end surface of front end plate 22 by a plurality of bolts 13.
  • An opening in cup shaped casing 12 is covered by front end plate 11 to seal off inner chamber 14 of cup shaped casing 12.
  • An opening 111 is formed in the center of front end plate 11 for penetration or passage of a drive shaft 15.
  • Front end plate 11 has an annular sleeve 16 projecting from the front end surface thereof which surrounds drive shaft 15. In the embodiment shown in Fig. 1, sleeve 16 is separated from front end plate 11. Therefore, sleeve 16 is fixed to the front end surface of front end plate 11 by bolts 13 with cup shaped casing 12.
  • a pulley 17 is rotatably supported by a bearing 18 which is carried on the outer surface of sleeve 16.
  • the outer end portion of drive shaft 15, which extends from sleeve 16, is fixed on pulley 17 by a key 19 and bolt 20 through shims 21.
  • Drive shaft 15 is thus driven by an external drive power sauce through pulley 17.
  • a fixed spiral element 122 is formed integral with end plate portion 121 of cup shaped casing 12 and extends into inner chamber 14 of cup shaped casing 12.
  • Spiral element 122 which has approximately 1 and 3/4 turns or revolutions, has a trapezoidal shaped as shown in Fig. 1.
  • An outlet port 123 is formed through the end plate portion 121 of cup shaped casing 12 and an inlet port 124 is formed through the outer peripheral surface of cup shaped casing 12.
  • An orbiting scroll 22 is also located within inner chamber 14 of cup shaped casing 12 and includes a circular end plate 221 and orbital wrap or spiral element 222 affixed to or extending from one side surface of end plate 221.
  • a tubular member 223 projects axially from a generally center area of the side surface of end plate 221. Fixed spiral element 122 and orbiting spiral element 222 interfit at an angular offset of 180 0 and a predetermined radial offset. At least a pair of fluid pockets are defined between spiral elements 122 and 222.
  • Tubular member 223 has a hollow interior 224. extending through its center.
  • Drive shaft 15 has a disk shaped rotor 151 at its inner end which is rotatably supported by front end plate 11 through a bearing 23 located within opening 111 of front end plate 11.
  • a crank pin 152 projects axially from an axial end surface of rotor 151 at a position which is radially offset from the center of drive shaft 15.
  • Crank pin 152 is carried in hollow interior 224 of tubular member 223 by a bearing 24.
  • Bearing 24 is held within a ledge in hollow interior 224 by a snap ring 25 and a projection 225 formed on the inner surface of hollow interior 224.
  • Snap ring 25 is attached on the inner end of crank pin 152 and a spring washer 26 is placed between snap ring 25 and bearing 24. Accordingly, orbiting scroll 22 is pushed against front end plate 11 by spring washer 26.
  • a rotation preventing/thrust bearing device 28 is located between the-inner end surface of front end plate 11 and an axial end surface of end plate 221 of orbiting scroll 22.
  • Rotation preventing/thrust bearing device 28 includes a plurality'of fixed indentations 281 formed on the inner end surface of front end plate 11, a plurality of orbiting indentations 282 formed on the axial end surface of end plate 221 and, a plurality of bearing elements 283, such as balls.
  • Each ball 283 is placed in facing, generally aligned indentations 281 and 282. The rotation of orbiting scroll 22 is prevented by the interaction between balls 283 and indentations 281 and 282; also the axial thrust load from orbiting scroll 22 is supported by front end plate 11 through balls 283.
  • front end plate 11 and orbiting scroll 22 are formed of light alloy metal, for example, aluminum alloy, to reduce the weight of the apparatus.
  • fixed and orbiting cover plate 284 and 285 are disposed on the inner end surface of front end plate 11 and the end surface of end plate 221 to prevent wear of indentations 281 and 282.
  • a grease seal mechanism 29 is placed between the outer peripheral portion of end plate 221 of orbiting scroll 22 and the inner end surface of front end plate 11. Also, bearing 24 which is located at hollow interior 224 of tubular member 223 and bearing 23 which is located within opening 111 have a grease seal mechanism. Therefore, a space defined by front end plate 11 and axial end surface of end plate 221 is sealed off. Grease, which is enclosed within space, is retained to lubricate rotation preventing/ thrust bearing device 28.
  • a connecting hole 31 is formed through end plate portion 121 of cup shaped casing 12.
  • Connecting hole 31 connects between a suction space 141 of inner chamber 14, which is defined between outer side wall of orbiting spiral element 222 and the inner side wall of cup shaped casing 12, and a center space 125 of both spiral elements 122 and 222.
  • Connecting hole 31 is formed in a circular shape as shown in Figs. ' 2a-2d, however, hole 31 may be formed in an ellipse shape as shown in Fig. 3.
  • a valve member 32 is seated in connecting hole 31 for closing hole 31. Valve member 32 is connected to a solenoid 33 through a planger 34.
  • solenoid 33 and planger 34 are located within a housing 125 which is formed integral with cup shaped casing 12.
  • a space 36 in which solenoid 33 and planger 34 are located is connected to outlet port 123 through a hole 37.
  • FIG. 2a fixed spiral element 122 and orbiting spiral element 222 interfit at an angular and radial offset with a small radial gap.
  • the fluid for example, the air introduced through inlet port 124 flows into suction space 141 of inner chamber 14 of cup shaped casing 12, and into a space A formed by the inner side wall of orbiting spiral element 222 and the outer side wall of fixed spiral element 122 and a space B formed by the outer side wall of orbiting spiral element 222 and the inner sidewall of fixed spiral element 122.
  • the relative position of the spiral elements after the drive shaft 15 rotates 90° is shown in Fig. 2b.
  • Fig. 4 shows another embodiment of this invention in which the configuration of the connecting hole and the control mechanism of hole are modified. Similar parts are represented by the same reference numerals as in embodiment shown in Fig. 1.
  • Solenoid 33 is fixed on the outside of cup shaped casing 12.
  • Connecting hole 31 formed through end plate portion 121 has a certain axial length and valve 32 is movably fitted within connecting hole 31.
  • Valve 32 is axially moved within connecting hole by operation of solenoid 33, so as to form a fluid passageway connecting between suction space 141 and center space 125 along the inner surface of the valve 32.
  • the fluid passageway for leaking compressed fluid to suction space 141 is controlled by movement of valve 32.
  • the displacement volume of the apparatus is thus controlled.

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP19820302818 1981-05-30 1982-06-01 Einrichtung vom Spiraltyp zum Fördern von Fluid Expired EP0070617B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP83209/81 1981-05-30
JP8320981A JPS57198386A (en) 1981-05-30 1981-05-30 Scroll type fluid system

Publications (3)

Publication Number Publication Date
EP0070617A2 true EP0070617A2 (de) 1983-01-26
EP0070617A3 EP0070617A3 (en) 1983-03-09
EP0070617B1 EP0070617B1 (de) 1985-04-10

Family

ID=13795926

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19820302818 Expired EP0070617B1 (de) 1981-05-30 1982-06-01 Einrichtung vom Spiraltyp zum Fördern von Fluid

Country Status (4)

Country Link
EP (1) EP0070617B1 (de)
JP (1) JPS57198386A (de)
AU (1) AU552132B2 (de)
DE (1) DE3262964D1 (de)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2146075A (en) * 1983-09-07 1985-04-11 Sanden Corp Scroll type compressor with displacement adjusting mechanism
EP0144169A2 (de) * 1983-11-08 1985-06-12 Sanden Corporation Verdichter mit spiralförmigem Förderraum und einstellbarer Förderleistung

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5490769A (en) * 1993-01-15 1996-02-13 Sanden International (U.S.A.), Inc. Variable capacity scroll type fluid displacement apparatus
JP6007737B2 (ja) * 2012-11-13 2016-10-12 株式会社豊田自動織機 スクロール型圧縮機

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2311936A (en) * 1941-04-01 1943-02-23 Gen Motors Corp Engine blower control
DE911078C (de) * 1951-09-14 1954-05-10 Otto Elwert Dipl Ing Zweitakt-Brennkraftmaschine mit Kurbelkastenpumpe und Spuelgeblaese
DE1071412B (de) * 1959-12-17 Fa. Fried. Krupp, Essen Verfahren zum Spülen und Aufladen der Zylinder von Zweitaktbrennkraftmaschinen, insbesondere Zweitaktdieselmotoren, und Einrichtung zur Durchführung dieses Verfahrens
DE2004749A1 (de) * 1970-02-03 1971-08-12 Krag, Jep Reuter, 4500 Osnabrück Elektrolader zur Verbesserung des Fullungs grades bei Ottomotoren
US4141677A (en) * 1977-08-15 1979-02-27 Ingersoll-Rand Company Scroll-type two stage positive fluid-displacement apparatus with intercooler
DE2945570A1 (de) * 1978-12-26 1980-07-10 Caterpillar Tractor Co Turbolader-bypass-steuerung

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1071412B (de) * 1959-12-17 Fa. Fried. Krupp, Essen Verfahren zum Spülen und Aufladen der Zylinder von Zweitaktbrennkraftmaschinen, insbesondere Zweitaktdieselmotoren, und Einrichtung zur Durchführung dieses Verfahrens
US2311936A (en) * 1941-04-01 1943-02-23 Gen Motors Corp Engine blower control
DE911078C (de) * 1951-09-14 1954-05-10 Otto Elwert Dipl Ing Zweitakt-Brennkraftmaschine mit Kurbelkastenpumpe und Spuelgeblaese
DE2004749A1 (de) * 1970-02-03 1971-08-12 Krag, Jep Reuter, 4500 Osnabrück Elektrolader zur Verbesserung des Fullungs grades bei Ottomotoren
US4141677A (en) * 1977-08-15 1979-02-27 Ingersoll-Rand Company Scroll-type two stage positive fluid-displacement apparatus with intercooler
DE2945570A1 (de) * 1978-12-26 1980-07-10 Caterpillar Tractor Co Turbolader-bypass-steuerung

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2146075A (en) * 1983-09-07 1985-04-11 Sanden Corp Scroll type compressor with displacement adjusting mechanism
EP0144169A2 (de) * 1983-11-08 1985-06-12 Sanden Corporation Verdichter mit spiralförmigem Förderraum und einstellbarer Förderleistung
EP0144169A3 (en) * 1983-11-08 1986-12-10 Sanden Corporation Scroll type compressor with displacement adjusting mechanism

Also Published As

Publication number Publication date
AU552132B2 (en) 1986-05-22
JPS57198386A (en) 1982-12-04
EP0070617A3 (en) 1983-03-09
DE3262964D1 (en) 1985-05-15
EP0070617B1 (de) 1985-04-10
AU8434582A (en) 1982-12-09

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