EP0105981A1 - Appareil à déplacement de fluide à volutes imbriquées - Google Patents

Appareil à déplacement de fluide à volutes imbriquées Download PDF

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Publication number
EP0105981A1
EP0105981A1 EP82305402A EP82305402A EP0105981A1 EP 0105981 A1 EP0105981 A1 EP 0105981A1 EP 82305402 A EP82305402 A EP 82305402A EP 82305402 A EP82305402 A EP 82305402A EP 0105981 A1 EP0105981 A1 EP 0105981A1
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EP
European Patent Office
Prior art keywords
indicator
fluid
center
end plate
receptacle
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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Withdrawn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
EP82305402A
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German (de)
English (en)
Inventor
Masaharu Hiraga
Yuji Yoshii
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
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Sanden Corp
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Filing date
Publication date
Application filed by Sanden Corp filed Critical Sanden Corp
Priority to EP82305402A priority Critical patent/EP0105981A1/fr
Publication of EP0105981A1 publication Critical patent/EP0105981A1/fr
Withdrawn legal-status Critical Current

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    • 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
    • F01C1/00—Rotary-piston machines or engines
    • F01C1/02—Rotary-piston machines or engines 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
    • F01C1/0207—Rotary-piston machines or engines 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
    • F01C1/0215—Rotary-piston machines or engines 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

  • This invention relates to a fluid displacement apparatus, and more particularly to a scroll type fluid displacement apparatus.
  • Scroll type fluid displacement apparatus are well known in the prior art.
  • U.S. Patent No. 801,182 discloses a device including two scroll memebers each having a circular end plate and a spiroidal or involute spiral element. These scroll members 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 a pair of fluid pockets.
  • the relative orbital motion of the two scroll members shifts the line contacts along the spiral curved surfaces and, therefore, the fluid pockets change in volume. Since the volume of the 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.
  • a scroll type fluid displacement apparatus includes a housing having a fluid inlet port and fluid outlet port.
  • a fixed scroll is joined with the housing and has a first circular end plate from which a first wrap extends.
  • An orbiting scroll has a second circular 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 sealed off fluid pockets.
  • a driving mechanism which includes a drive shaft, is operatively connected to the orbiting scroll to effect the orbital motion of the orbiting scroll at radius Ror, while the rotation of the orbiting scroll is prevented by a rotation preventing/thrust bearing means, whereby the fluid in the fluid pockets moves inwardly or outwardly and changes in volume.
  • the center of the first circular end plate is aligned with the center line of the housing and the center of the first wrap is radially offset from the center of the first circular end plate by the distance 1/2 Ror.
  • the center of the second wrap is radially offset from the center of the second circular end plate by the distance 1/2 Ror.
  • the drive shaft has a center line, which is aligned with the center line of the housing, and also has a crank pin, the center line of which is aligned with the center of the second circular end plate.
  • Figs. la-ld may be considered end views of a compressor wherein the end plates are removed and only spiral elements are shown at orbital angular positions spaced 90° from one another.
  • Two spiral elements 1 and 2 are angularly offset and interfitted with one another.
  • the orbiting spiral element 1 and fixed spiral element 2 make four line contacts as shown at four points A-D.
  • a pair of fluid pockets 3a and 3b are defined between line contacts D, C and line contacts A, B as shown by the dotted regions.
  • the fluid pockets are defined not only by the wall of spiral elements 1 and 2, but also by the end plates from which these spiral elements 1 and 2 extend.
  • Orbiting spiral element 1 is moved in relation to fixed spiral element 2 so that the center 0' of orbiting spiral element 1 revolves around the center 0 of fixed spiral element 2 at a radius of 0-0', while the rotation of orbiting spiral element 1 is prevented.
  • This motion angularly and radially shifts fluid pockets 3a and 3b toward the center of the interfitted spiral elements, to gradually reduce the volume of each fluid pocket 3a and 3b, as shown in Fig. la-ld, thereby, compressing the fluid in each pocket.
  • fluid pockets 3a, 3b are initially formed when the ends of spiral elements 1,2 contact with the outer surface of the other spiral elements, as shown in Fig. la. Further rotation of orbiting spiral element 1 causes the pockets 3a, 3b to reduce in volume, as shown in Figs. lb, lc. Thereafter, the pair of fluid pockets 3a, 3b become connected to one another, as shown in Fig. Id, and the single pocket is further reduced in volume, as shown by the- undotted central area in Figs. la, lb and 1c. During the reduction in volume of pockets 3a, 3b, the ends of the spiral elements leave contact with the outer surface of the other spiral elements, as shown in Figs. lb, 1c, ld, until contact is reestablished, as shown in Fig. la to form a new pair of fluid pockets 3a, 3b.
  • a scroll type fluid displacement apparatus In comparison with conventional fluid displacement apparatus of the piston type, a scroll type fluid displacement apparatus has several advantages, such as continuous transfer of the fluid, volume efficiency, and relatively silent operation.
  • a cylindrical housing is an advantageous configuration for containing a pair of scroll members each of which have a wall thickness t and involute angle ⁇ .
  • An optimal disposition of the end plate and spiral element to reduce the diameter of the housing is disclosed in U. S. Patent No. 4,304,535 (Terauchi), the disclosure of which is incorporated herein. Accordingly, as shown in Figs. 2 and 3 herein, orbiting scroll 231 orbits at radius Ror while maintaining its angular orientation with fixed scroll 221.
  • the sectional area of the housing needed to permit the orbital motion of orbiting scroll 231 at radius Ror will be made up by adding the spiral or snail shaped area on which fixed spiral element is held (area D in Fig. 3) to the space (area B in Fig.
  • the inner diameter of the cylindrical housing in which the pair of scrolls are contained will be given by 2 ⁇ rg+t+Ror, where rg is involute generating circle radius.
  • the center of inner wall of cylindrical housing is radially offset from the center of involute generating circle of fixed spiral element and the maximum diameter of orbiting end plate to permit the orbital motion within the above cylindrical housing will be given by 26rg+t+Ror.
  • a suitable drive point of the orbiting scroll is the involute generating circle center of the orbiting spiral element, since the relation between the center of tangential gas force in the high pressure fluid pocket defined by both scroll centers and the drive point does not change at any rotational angle of the drive shaft.
  • the center of drive shaft is concentric with the involute generating circle center OF of fixed spiral element 222' and the drive point O D of orbiting scroll 231 is disposed on the involute generating circle center Oo of orbiting spiral element 232'.
  • Orbiting scroll 231 therefore revolves at a radius O F -Oo and this radial spacing does not change during the operation of the apparatus.
  • Fig. 4 illustrates the relationship between the center of each end plate and the centers of the involute generating circles of the spiral elements.
  • the center O E of orbiting end plate 231' is radially offset from the involute generating circle center Oo of orbiting spiral element 232' to the right by a distance 1/2 Ror.
  • the center Oc of fixed end plate 221' i.e., the center of the compressor housing is radially offset from the involute generating circle center OF of fixed spiral element 222' to the right by a distance 1/2 Ror.
  • the center Oc is also radially offset from the center Oo by a distance 1/2 Ror.
  • the drive point O D is disposed on the center Oo and the center Od of drive shaft 13 is concentric with center O F , whereby the orbital motion of the orbiting scroll 231 is shown as the locus of the center Oo.
  • the locus of the center Oo is shown by the circle C with its center at center OF of drive shaft, as shown in Fig. 4.
  • Fig. 5 is a vertical sectional view of a scroll type compressor which utilizes the above mentioned disposition of scroll members.
  • the center OF of the drive shaft 13' is radially offset from the center Oc of housing 10' and also the center Oo of the drive point is radially offset from the center 0 E of orbiting end plate 231'. Therefore, a tubular boss 233' projecting axially from one end surface of end plate 231' and rotatably supported on a drive pin of the driving mechanism is radially offset from the center of end plate 231'. Tubular boss 233' therefore must be formed at an offset position. The forming of these scrolls is complicated, and hence, it is difficult to form the scrolls with high dimensional accuracy.
  • a coupling mechanism 24' is required to maintain the angular orientation between both scrolls and to carry the radial force from the orbiting scroll.
  • the coupling mechanism such as a ball coupling/thrust bearing device, must be disposed within the housing 10' at a radially offset position.
  • Ring member 241' which is concentric with the ball coupling/thrust bearing device is fitted on the inner end surface of the housing 10' at a radially offset position, thereby requiring a dead space A on which the outer peripheral portion of ring member 241' is placed.
  • the diameter of housing 10' is increased, as shown in Fig. 5.
  • the compressor includes a compressor housing 10 having a front end plate 11 and a cup shaped casing 12 fastened to an end surface of front end plate 11.
  • An opening 111 the center of which is concentric with the center line of cup shaped casing 12 is formed in the center of front end plate 11 for supporting a drive shaft 13.
  • the center line of drive shaft 13 is thus concentric or aligned with the center line of cup shaped casing 12, ie. with the center line of the housing.
  • An annular projection 112, concentric with opening 111, is formed on the rear surface of front end plate 11 and faces cup shaped casing 12.
  • annular projection 112 contacts an inner wall of the opening of cup shaped casing 12.
  • Cup shaped casing 12 is fixed on the rear end surface of front end plate 11 by a fastening device, such as bolts and nuts (not shown), so that the opening of cup shaped casing 12 is covered by front end plate 11.
  • An O-ring 14 is placed between the outer peripheral surface of annular projection 112 and the inner wall of cup shaped casing 12 to seal the mating surfaces between front end plate 11 and cup shaped casing 11.
  • Front end plate 11 has an annular sleeve 15 projecting from its front end surface.
  • Sleeve 15 surrounds drive shaft 13 to define a shaft seal cavity.
  • a shaft seal assembly 16 is assembled on drive shaft 13 within the shaft seal cavity.
  • Sleeve 15 is attached to the front end surface of front end plate 11 by screws (not shown).
  • An O-ring 17 is placed between the front end surface of front end plate 11 and an end surface of sleeve 15 to seal the mating surfaces of front end plate 11 and annular sleeve 15.
  • sleeve 15 may be formed integral with front end plate 11.
  • a pulley 18 is rotatably supported by a bearing 19 on the outer surface of sleeve 15.
  • An electromagnetic coil 20, which is received in an annular cavity of pulley 18, is mounted on the outer surface of sleeve 15 by a support plate 201.
  • An armature plate 21 is elastically supported on the outer end of drive shaft 13 which extends from sleeve 15.
  • a magnetic clutch is formed by pulley 18, magnetic coil 20 and armature plate 21.
  • Drive shaft 13 is thus driven by an external power source, for example, an engine of vehicle, through a rotation transmitting device, such as the above described magnetic clutch.
  • a number of elements are located within the inner chamber of cup shaped casing 12 including a fixed scroll 22, an orbiting scroll 23, a driving mechanism for orbiting scroll 23 and a rotation preventing/thrust bearing device 24 for orbiting scroll 23.
  • the inner chamber of cup shaped casing 12 is formed between the inner wall of cup shaped casing 12 and the rear end surface of front end plate 11.
  • Fixed scroll 22 includes a circular end plate 221, and a wrap or spiral element 222 affixed to or extending from one end surface of end plate 221.
  • a plurality of internal bosses 223 axially project from the end surface of end plate 221 on the side opposite spiral element 222.
  • the center of spiral element 222 (the center of its involute generating circle) is radially offset from the center of end plate 221 by a distance Ror/2 wherein Ror is the radius at which orbiting scroll 23 orbits.
  • the end surface of each boss 223 is seated on the inner surface of end plate portion 121 of cup shaped casing 12 and is fixed to end plate portion 121 by a plurality of bolts 25, one of which is shown in Fig. 6.
  • Circular end plate 221 of fixed scroll 22 partitions the inner chamber of cup shaped casing 12 into a discharge chamber 26 having bosses 223, and a suction chamber 27, in which spiral element 222 of fixed scroll 22 is located.
  • a sealing member 28 is disposed within a circumferential groove 224 of circular end plate 221 to form a seal between the inner wall of cup shaped casing 12 and the outer wall of circular end plate 221.
  • Orbiting scroll 23 which is located in suction chamber 27, includes a circular end plate 231 and a wrap or spiral element 232 affixed to or extending from one end surface of end plate 231.
  • the center of spiral element 232 (the center of its involute generating circle ) is radially offset from the center of end plate 231 by a distance of Ror/2.
  • the spiral elements 222 and 232 interfit at angular offset of 180 0 and predetermined radial offset.
  • the spiral elements define at least a pair of fluid pockets between their interfitting surfaces.
  • Orbiting scroll 23 is connected to the driving mechanism and rotation preventing/thrust bearing device 24 to effect the orbital motion at a circular radius Ror by the rotation of drive shaft 13 to thereby compress fluid passing through the compressor.
  • radius Ror of orbital motion given by:
  • the pitch (p) of the spiral elements can be defined by 2 ⁇ rg, where rg is the involute generating circle radius.
  • the radius Ror of orbital motion is also illustrated in Fig. 10, as a locus of an arbitrary point Q on orbiting scroll 23.
  • the center of spiral element 232 is placed radially offset from the center of spiral element 222 by the distance Ror. Thereby, orbiting scroll 23 is allowed to undergo orbital motion at a radius Ror by the rotation of drive shaft 13.
  • fluid in the fluid pockets is compressed and the compressed fluid is discharged into discharge chamber 26 from the fluid pocket at the spiral elements center through a hole 225, and therefrom, discharged through fluid outlet port 30 on cup shaped casing 12 to an external fluid circuit, for example, a cooling circuit.
  • Drive shaft 13 is formed with a disk shaped rotor 131 at its inner end portion and is rotatably supported by sleeve 15 through a bearing 31 which is disposed within sleeve 15. Disk shaped rotor 131 is also rotatably supported by front end plate 11 through a bearing 32 located within opening 111 of front end plate 11.
  • a crank pin or drive pin 132 projects axially from an axial end surface of disk shaped rotor 131 and is radially offset from the center of drive shaft 13.
  • Circular end plate 231 of orbiting scroll 23 has tubular boss 233 axially projecting from the end surface opposite to the end surface from which spiral element 232 extends.
  • a discoid or short axial bushing 33 fits into boss 233, and is rotatably supported therein by a bearing, such as needle bearing 34.
  • An eccentric hole 35 is formed on bushing 33; eccentric hole 35 is radially offset from the center of bushing 33.
  • Drive pin 132 which is surrounded by a bearing 36, fits into eccentric hole 35. Therefore, bushing 33 is driven by the revolution of drive pin 132 to thereby rotate within bearing 34.
  • the spiral element 232 of orbiting scroll 23 is pushed against the spiral element 222 of fixed scroll 22 due to. the moment created between the driving point and the reaction force acting point of the pressurized gas to secure the line contacts and effect radial sealing.
  • Rotation preventing/thrust bearing device 24 is placed between the inner end surface of front end plate 11 and the end surface of circular end plate 231 which faces the inner end surface of front end plate 11.
  • Rotation preventing/thrust bearing device 24 includes a fixed ring 241, which is fastened against the inner end surface of front end plate 11 by a fastening device, such as pins 242, an orbiting ring 243 which is fastened against the end surface of circular end plate 231 by a fastening device, such as pins 244, and a bearing element, such as a plurality of spherical balls 245.
  • Both rings 241 and 243 have a plurality of circular indentations 246 and 247 and one of the spherical balls 245 is retained between each of these indentations 246 and 247.
  • the rotation of orbiting scroll 23 is prevented by balls 245, which interact with the edges of indentations 246 and 247 to prevent rotation.
  • balls 245. carry the axial thrust load from orbiting scroll 23. Therefore, orbiting scroll 23 orbits while maintaining its angular orientation to fixed scroll 22.
  • orbiting ring 243 preferably consists of a ring member 243A and plate member 243B. Both members 243A and B are fastened against end plate 231 of orbiting scroll 23 by pins 244.
  • orbiting ring 243 may be formed of a single integral piece of material.
  • Fig. 9 The relative locations of the centers of the spiral elements 222 and 232, circular end plates 221 and 231, housing 10, drive shaft 13 and drive pin 132, in accordance with the present invention, are illustrated in Fig. 9.
  • the center Oc of the end plate 221 of fixed scroll 22 is concentric or aligned with the center line 0 s of the housing 10, which is also the center line of drive shaft 13.
  • the drive point 0 D of orbiting scroll 23 is placed on the center O E of the end plate 231 of orbiting scroll 23.
  • the dead space which is caused by the eccentric disposition (shown as A in Fig. 5) can be eliminated and the diameter of the housing can be reduced. Since, the disposition of the driving mechanism or the rotation preventing/thrust bearing devices is concentric to the connected parts, the manufacturing of the parts, for example the orbiting scroll and the front end plate, can be done by simple working of the parts to a high dimensional accuracy. Furthermore, the assembly of the apparatus utilizing such concentric parts is simple.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Rotary Pumps (AREA)
EP82305402A 1982-10-11 1982-10-11 Appareil à déplacement de fluide à volutes imbriquées Withdrawn EP0105981A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP82305402A EP0105981A1 (fr) 1982-10-11 1982-10-11 Appareil à déplacement de fluide à volutes imbriquées

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP82305402A EP0105981A1 (fr) 1982-10-11 1982-10-11 Appareil à déplacement de fluide à volutes imbriquées

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EP0105981A1 true EP0105981A1 (fr) 1984-04-25

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013181506A (ja) * 2012-03-02 2013-09-12 Yanmar Co Ltd スクロール形流体機械

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0009355A1 (fr) * 1978-09-09 1980-04-02 Sanden Corporation Compresseurs du type à spirale
EP0010402A1 (fr) * 1978-10-12 1980-04-30 Sanden Corporation Perfectionnements aux compresseurs du type à spirale
DE3013785A1 (de) * 1979-04-11 1981-03-12 Hitachi, Ltd., Tokyo Schrauben-arbeitsmaschine
EP0039622A1 (fr) * 1980-05-07 1981-11-11 Sanden Corporation Machines à déplacement de fluide

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0009355A1 (fr) * 1978-09-09 1980-04-02 Sanden Corporation Compresseurs du type à spirale
EP0010402A1 (fr) * 1978-10-12 1980-04-30 Sanden Corporation Perfectionnements aux compresseurs du type à spirale
DE3013785A1 (de) * 1979-04-11 1981-03-12 Hitachi, Ltd., Tokyo Schrauben-arbeitsmaschine
EP0039622A1 (fr) * 1980-05-07 1981-11-11 Sanden Corporation Machines à déplacement de fluide

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2013181506A (ja) * 2012-03-02 2013-09-12 Yanmar Co Ltd スクロール形流体機械

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Inventor name: HIRAGA, MASAHARU