EP0201774B1 - Machine à piston rotatif à déplacement positif - Google Patents

Machine à piston rotatif à déplacement positif Download PDF

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Publication number
EP0201774B1
EP0201774B1 EP86105671A EP86105671A EP0201774B1 EP 0201774 B1 EP0201774 B1 EP 0201774B1 EP 86105671 A EP86105671 A EP 86105671A EP 86105671 A EP86105671 A EP 86105671A EP 0201774 B1 EP0201774 B1 EP 0201774B1
Authority
EP
European Patent Office
Prior art keywords
rotor
housing
spiral
displacers
delivery chambers
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
Application number
EP86105671A
Other languages
German (de)
English (en)
Other versions
EP0201774A1 (fr
Inventor
Heinrich Güttinger
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.)
BBC Brown Boveri AG Switzerland
Aginfor AG
Original Assignee
BBC Brown Boveri AG Switzerland
Aginfor AG fuer industrielle Forschung
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 BBC Brown Boveri AG Switzerland, Aginfor AG fuer industrielle Forschung filed Critical BBC Brown Boveri AG Switzerland
Priority to AT86105671T priority Critical patent/ATE36895T1/de
Publication of EP0201774A1 publication Critical patent/EP0201774A1/fr
Application granted granted Critical
Publication of EP0201774B1 publication Critical patent/EP0201774B1/fr
Expired legal-status Critical Current

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Classifications

    • 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
    • F01C1/0223—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 with symmetrical double wraps
    • 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
    • F01C1/0246—Details concerning the involute wraps or their base, e.g. geometry
    • 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
    • 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

Definitions

  • the invention relates to a rotary piston displacement machine for compressible media
  • spiral-like conveying spaces and displacers each consist of two sections, with a second section continuously adjoining the outlet-side end of a first section spanning less than 360 °, the radius of curvature of which is considerably smaller than the smallest radius of curvature of the first section.
  • Such a displacement machine is suitable for charging an internal combustion engine, since it is characterized by an almost pulsation-free conveyance of the working medium, which consists, for example, of air or an air / fuel mixture.
  • the working medium which consists, for example, of air or an air / fuel mixture.
  • a machine of the type mentioned is known from DE-3 141 525 A1.
  • This compressor With this compressor, two displacers mounted on a rotor mesh with each other.
  • the associated conveying spaces in the fixed housing each run from an inlet space provided on the outer periphery of the housing to an outlet space provided on the inner periphery of the housing, via which the compressed working medium is discharged.
  • the centrally arranged drive shaft for the rotor together with a part of the shaft bearing and the rotor bearings is also housed in the interior of the housing.
  • the present invention is therefore based on the object of providing a displacement machine of the type mentioned at the outset, in which heat can be dissipated during the compression.
  • the advantage of the invention is, on the one hand, that the drive bearings are now in the suction area of the spirals and are therefore cooled with fresh air, which is an important prerequisite for maintenance-free or at least low-maintenance bearings.
  • the spiral arrangement due to the spiral arrangement, access for the cooling medium to the hot part of the spirals, which is favorable for heat dissipation during compression, is achieved, so that, if it is intended to be used as a charging device for internal combustion engines, a separate after-cooling of the charge air can be dispensed with.
  • the housing is expediently provided with cooling fins all around.
  • the machine which is represented in approximately 80% of its natural size, is equipped with two conveying rooms on each rotor side.
  • the direction of flow of the working medium, for example air, is indicated by arrows.
  • the cut surface of the rotor is not hatched in FIG. 3, however, the spiral cutters which have not been cut are shown in dotted lines.
  • the fixed housing is composed of the drive-side part housing 1 and the air-side part housing 2, which are screwed together via several flanges 3 attached to the housing periphery.
  • the two delivery rooms 4 are behind Type of a spiral slot incorporated. These conveying spaces each run from an inlet 5 arranged at the outer spiral end to an outlet 6 arranged at the inner spiral end.
  • the two inlets 5 and the outlets 6 communicate with one another in a manner not shown and are each provided with an air inlet 9 or air outlet on the partial housing 2 on the air side.
  • Air outlet 10 connected (Fig. 2).
  • the conveying spaces 4 have parallel circumferential walls 7, 8 which are arranged at a constant distance from one another and which comprise a spiral of more than 360 °.
  • the spiral is composed of two sections, which are explained in FIG. 1 using the example of the outer peripheral wall 8 of the lower spiral:
  • this first circular arc spans an angle of approximately 240 ° with its center 15 and begins at the inlet-side end of the delivery chamber 4.
  • a second section 40 also continuously adjoins in the form of a circular arc with the center 33, which here encompasses an angle of approximately 180 °.
  • the radius of curvature of the second section 40 ′′ is substantially smaller than that of the first section 40 ′.
  • the entire second section 40 ′′ finds space between the outlet-side end of the first section 40 ′ and its center 15.
  • the disk-shaped rotor is designated as a whole by 11.
  • Spiral-shaped displacers 13 are provided on both sides of the disk 12 and are arranged as band-shaped strips on the disk. These displacers 13 are held between the peripheral walls 7, 8 of the delivery spaces 4. Their curvature is dimensioned such that they almost touch the inner peripheral walls 7 and the outer peripheral walls 8 at several points B1, B2 and B3 at the same time.
  • the centers 14 of the two displacers 13 are offset eccentrically with respect to the centers 15 of the two delivery spaces 4 (FIG. 1). It is understood that the displacers 13 must have the same geometry as the delivery spaces, i.e. form a spiral consisting of two circular sections 130 ′, 130 ′′ with the centers 14, 34, which comprises more than 360 °.
  • the displacers 13 and thus the rotor 11 are mounted and guided in order to carry out a circular, rotation-free movement.
  • the rotor is arranged on an eccentric disk 17 by means of a ball bearing 16.
  • This eccentric disc sits on a drive shaft 18, which in turn is mounted in the fixed housing in ball bearings 19, 20, 21 and 22. Not shown is the drive of the shaft 18, which usually takes place via a V-belt pulley. To compensate for the inertial forces arising when the rotor 11 is eccentrically driven, bearings 19 and 20, respectively. 21 and 22 arranged on the drive shaft counterweights 23.
  • the eccentric drive of the disk-shaped rotor having the displacers results in a circular movement of each of the points of the displacers, this circular movement being limited by the peripheral walls of the delivery spaces.
  • crescent-shaped work spaces 24, which contain the working medium result on both sides of the displacers, which are advanced as a result of the eccentric movement through the delivery spaces in the direction of the respective outlet 6.
  • the volume of these working spaces is reduced and the pressure of the working fluid increases accordingly.
  • shaft bearings 19 to 22 are located all around in the intake area and are accordingly cooled with fresh air.
  • the centers 14, 15 of the first spiral sections 40 ', 130' are located approximately in the middle between the machine axis and the outlets 6, which results in a very space-saving spiral configuration.
  • the air is thus conveyed from the inside to the outside, making the machine parts heated during the compression process very easy to cool.
  • the outer peripheral walls 8 of the hot spiral sections are provided with cooling fins 27 throughout.
  • the two housing parts 1, 2 are expediently equipped with such cooling fins over their entire circumference (FIG. 1).
  • the rotor disk 12 In order to guide the sucked in working fluid from the air-side to the drive-side delivery areas, respectively. To discharge in the opposite direction, the rotor disk 12 is provided with openings 28 of corresponding shape in the area of the inlets 5 and outlets 6 (FIG. 3).
  • the compressed air in the outlet 10 has the same state throughout, since it is always a mixture of an inner working chamber 24 'and an outer working chamber 24 ".
  • the eccentric disk 17 is namely aligned in this way on the drive shaft 18, that - as in the example in FIG. 1 - the points B1 and B2 (of the two displacers 13 with the peripheral walls of the conveying spaces 4), the centers 14, 15 of the two spirals and the axes 25, 26 of the drive shaft and eccentric disc in a certain position lie on a common line 29.
  • the displacer forms the narrowest gap with the outer peripheral wall 8, while in the lower spiral at point B2 it forms the inner peripheral wall 7 of the delivery chamber 4.
  • the central symmetrical spiral arrangement also compensates for the tilting moment which would arise when operating with a single spiral with the drive bearing moved from the center. This has the advantage that the device required for translatory guiding of the rotor 11 can be of simple design.
  • the runner is guided by means of four free-running roller bolts 30, which are distributed over the circumference of the machine. It is not necessary for the rolling pins to be on the same pitch circle, nor for them to have the same angular distances from one another. These freedoms allow the guide device to be accommodated in a space-saving manner without impairing the spiral course.
  • a rolling pin rolls in a bore 31 of the rotor and a matching, identical bore 32 in both housing parts 1, 2. So that the rolling pin is in a secure system at all times, its diameter is smaller by the eccentricity between the eccentric axis 26 and the drive axis 25 than the diameter of the housing bores 32.
  • the roller pin position shown in FIG. 3 corresponds to the displacer position in FIG. 1, in which the upper displacer almost touches the outer peripheral wall 8 of the delivery chamber 4 at point B2.
  • a fan could be mounted outside the housing on the drive shaft, for example, which forcibly ventilates the cooling fins during operation.
  • This fan could possibly also be arranged on the air side of the housing if, for example, the drive shaft were passed through the partial housing 2.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Geometry (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Reciprocating Pumps (AREA)
  • Supercharger (AREA)

Claims (5)

1. Machine à piston rotatif à déplacement positif pour des fluides compressibles,
- avec deux chambres de circulation (4) s'étendant en spirale dans un carter immobile (1, 2) et embrassant plus de 360°, qui conduisent chacune d'une entrée (5) à une sortie (6),
- avec un organe déplaceur (13) associé à chaque chambre de circulation en s'engageant dans celle-ci, s'étendant également en spirale et embrassant plus de 360°, qui est constitué par une pale en forme de bande montée sur un rotor (11) en forme de disque entraîné excentriquement par rapport au carter, et qui est supporté et guidé de façon à effectuer un mouvement circulaire sans torsion, par rapport aux chambres de circulation (4),
- dans laquelle les chambres de circulation (4) et les organes déplaceurs (13) en spirale se composent chacun de deux tronçons et où, à l'extrémité de sortie d'un premier tronçon (40', 130') embrassant moins de 360°, se raccorde de manière continue un second tronçon (40", 130") dont le rayon de courbure est sensiblement plus petit que le plus petit rayon de courbure du premier tronçon,
caractérisée en ce que:
- les au moins deux chambres de circulation (4) en spirale sont disposées en symétrie centrale l'une par rapport à l'autre, sans présenter de pôle commun, et que
- les extrémités des chambres de circulation (4), du côté d'entrée, sont disposées autour des paliers moteurs (19, 20, 21, 22) du rotor (11).
2. Machine suivant la revendication 1, caractérisée en ce que l'axe moteur (25) coïncide avec le centre de symétrie des chambres de circulation (4) et l'axe central (26) excentriquement déporté du rotor (11) coïncide avec le centre de symétrie des organes déplaceurs (13).
3. Machine suivant la revendication 1, caractérisée en ce que le carter (1, 2) est de préférence pourvu d'ailettes de refroidissement (27) sur tout son pourtour.
4. Machine à déplacement positif, dans laquelle le rotor (11) est équipé d'organes déplaceurs (13) sur les deux faces suivant la revendication 1, caractérisée en ce que le rotor (11) est pourvu de fenêtres (28) tant du côté de l'entrée que du côté de la sortie.
5. Machine suivant la revendication 1, caractérisée en ce que le rotor (11) est guidé dans le carter (1, 2) sur plusieurs boulons roulants (30) et où chacun des boulons roulants (30) est engagé dans un alésage (31) du rotor ainsi que dans un alésage (32) approprié et de même dimension du carter, le diamètre des boulons roulants (30) étant plus petit que celui des alésages (32) du carter d'une quantité égale à l'excentricité entre l'axe moteur (25) et l'axe central (26) du rotor.
EP86105671A 1985-04-26 1986-04-24 Machine à piston rotatif à déplacement positif Expired EP0201774B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86105671T ATE36895T1 (de) 1985-04-26 1986-04-24 Rotationskolben-verdraengungsarbeitsmaschine.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1780/85A CH667497A5 (de) 1985-04-26 1985-04-26 Rotationskolben-verdraengungsarbeitsmaschine.
CH1780/85 1985-04-26

Publications (2)

Publication Number Publication Date
EP0201774A1 EP0201774A1 (fr) 1986-11-20
EP0201774B1 true EP0201774B1 (fr) 1988-08-31

Family

ID=4218437

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86105671A Expired EP0201774B1 (fr) 1985-04-26 1986-04-24 Machine à piston rotatif à déplacement positif

Country Status (6)

Country Link
US (1) US4715797A (fr)
EP (1) EP0201774B1 (fr)
JP (1) JPS61250392A (fr)
AT (1) ATE36895T1 (fr)
CH (1) CH667497A5 (fr)
DE (1) DE3660636D1 (fr)

Families Citing this family (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3744866C2 (en) * 1987-08-12 1990-04-26 Dancho Zochev Dipl.-Ing. 1000 Berlin De Donkov Rotary piston compressor with radial channels
US5171140A (en) * 1990-10-19 1992-12-15 Volkswagen Ag Spiral displacement machine with angularly offset spiral vanes
DE59206416D1 (de) * 1991-12-05 1996-07-04 Aginfor Ag Verdrängermaschine nach dem Spiralprinzip
DE4215038A1 (de) * 1992-05-07 1993-11-11 Bitzer Kuehlmaschinenbau Gmbh Spiralverdichter für kompressible Medien
EP0579888B1 (fr) * 1992-07-20 1996-08-21 AGINFOR AG für industrielle Forschung Pompe rotatif à spirale
DE19500774A1 (de) * 1995-01-13 1996-07-18 Adolf Dr Ing Hupe Rotationskolbenmaschine
US5616015A (en) * 1995-06-07 1997-04-01 Varian Associates, Inc. High displacement rate, scroll-type, fluid handling apparatus
ATE229612T1 (de) * 1997-08-26 2002-12-15 Crt Common Rail Tech Ag Spiralverdrängermaschine für kompressible medien
WO2000049275A1 (fr) * 1999-02-18 2000-08-24 Fritz Spinnler Machine de refoulement construite selon le principe de la spirale
EP2179138B1 (fr) * 2007-07-26 2015-09-09 Spinnler Engineering Machine de déplacement de matière fonctionnant selon le principe de la spirale
DE102011103165A1 (de) * 2010-07-02 2012-01-05 Handtmann Systemtechnik Gmbh & Co. Kg Ladevorrichtung zur Verdichtung von Ladeluft für einen Verbrennungsmotor
US20150260091A1 (en) * 2014-03-14 2015-09-17 Chung-Shan Institute Of Science And Technology, Armaments Bureau, M.N.D External cooling fin for rotary engine
US20160305315A1 (en) * 2014-03-14 2016-10-20 National Chung_Shan Institute Of Science And Technology External cooling fin for rotary engine
EP4323649A4 (fr) * 2021-05-05 2024-08-14 Gazi Univ Compresseur scroll à palettes en spirale

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1041721A (en) * 1908-03-27 1912-10-22 John F Cooley Rotary engine.
US1209204A (en) * 1914-03-16 1916-12-19 James H Richards Rotary engine.
DE589419C (de) * 1932-02-17 1934-03-10 Heinrich Kretschmer Maschine mit kreisschwingendem Waelzkolben
US2112890A (en) * 1936-10-22 1938-04-05 Socony Vacuum Oil Co Inc Rotary power device
FR825643A (fr) * 1936-11-26 1938-03-09 Perfectionnements au capsulisme à excentrique
DE1064076B (de) * 1957-09-27 1959-08-27 Paul Lagemann Mehrzweck-Drehkolbenkraft- und Arbeitsmaschine mit zwei Verdraengungskammern fuer gasfoermige und fluessige Betriebsstoffe
DE1935621A1 (de) * 1968-07-22 1970-01-29 Leybold Heraeus Gmbh & Co Kg Verdraengerpumpe
CH561842A5 (fr) * 1971-12-10 1975-05-15 Aginfor Ag
CH555476A (de) * 1972-08-31 1974-10-31 Aginfor Ag Verdraengermaschine.
US4192152A (en) * 1978-04-14 1980-03-11 Arthur D. Little, Inc. Scroll-type fluid displacement apparatus with peripheral drive
JPS55112892A (en) * 1979-02-23 1980-09-01 Mitsubishi Electric Corp Scroll compressor
DE3138585A1 (de) * 1981-09-29 1983-07-21 Volkswagenwerk Ag, 3180 Wolfsburg Verdraengermaschine fuer kompressible medien
US4424010A (en) * 1981-10-19 1984-01-03 Arthur D. Little, Inc. Involute scroll-type positive displacement rotary fluid apparatus with orbiting guide means
DE3231756C2 (de) * 1982-08-26 1985-08-01 Pierburg Gmbh & Co Kg, 4040 Neuss Rotationskolbenmaschine für Fluide

Also Published As

Publication number Publication date
EP0201774A1 (fr) 1986-11-20
JPS61250392A (ja) 1986-11-07
CH667497A5 (de) 1988-10-14
US4715797A (en) 1987-12-29
DE3660636D1 (en) 1988-10-06
ATE36895T1 (de) 1988-09-15

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