EP0218806B1 - Machine à piston à axe interne - Google Patents

Machine à piston à axe interne Download PDF

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Publication number
EP0218806B1
EP0218806B1 EP86109613A EP86109613A EP0218806B1 EP 0218806 B1 EP0218806 B1 EP 0218806B1 EP 86109613 A EP86109613 A EP 86109613A EP 86109613 A EP86109613 A EP 86109613A EP 0218806 B1 EP0218806 B1 EP 0218806B1
Authority
EP
European Patent Office
Prior art keywords
sealing
sealing gaps
rotors
circumferential surfaces
internal rotor
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 - Lifetime
Application number
EP86109613A
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German (de)
English (en)
Other versions
EP0218806A1 (fr
Inventor
Otto Kraic
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.)
Individual
Original Assignee
Individual
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Filing date
Publication date
Application filed by Individual filed Critical Individual
Priority to AT86109613T priority Critical patent/ATE49626T1/de
Publication of EP0218806A1 publication Critical patent/EP0218806A1/fr
Application granted granted Critical
Publication of EP0218806B1 publication Critical patent/EP0218806B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • 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
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/082—Details specially related to intermeshing engagement type machines or engines
    • F01C1/084—Toothed wheels
    • 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
    • F01C1/08—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing
    • F01C1/10—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member
    • F01C1/103—Rotary-piston machines or engines of intermeshing engagement type, i.e. with engagement of co- operating members similar to that of toothed gearing of internal-axis type with the outer member having more teeth or tooth-equivalents, e.g. rollers, than the inner member the two members rotating simultaneously around their respective axes

Definitions

  • the invention relates to an internal-axis rotary lobe machine according to the preamble of claim 1.
  • Such a machine shows e.g. GB-A 316 295.
  • the dimensioning of the sealing gaps between the two runners represents an unsatisfactory compromise between the size of the sealing losses and the friction losses, whereby small sealing gaps, in addition to correspondingly high friction losses, also place high demands on the dimensionally accurate manufacture and assembly.
  • the object of the invention is to improve this compromise in a machine of this type by achieving a good seal between the rotors of the machine with relatively small losses at the sealing gaps. This object is achieved on the basis of the characterizing features of patent claim 1.
  • the improved compromise is based on the different evaluation of the different surface areas of the inner rotor when forming the sealing gap together with the outer rotor in order to seal the pressure side of the rotary piston machine from its side of low pressure, both with regard to the shape of the sealing gap or the surfaces forming it and also with regard to the meaning the local and temporal respective sealing gap position during the rotation of the rotor forming the sealing gap.
  • the outer circumference 4 of the outer rotor 2 surrounds the axis 5 of the inner rotor 3, which is fixed relative to the machine housing 1, and the axes 5, 6 of both rotors 2, 3 are arranged at a distance from one another.
  • the mutual arrangement of the rotors 2, 3 or their axes 5, 6 is consequently comparable to that on a gear with an internally toothed spur gear.
  • both runners 2 , 3 are located at a plurality of sealing points or sealing areas Di, D 2 , D 3 , D 4 , Ds. .. in a gap-forming approach to one another, and along two mutually opposite circumferential regions 10, 11 is the outer circumference 4 of the engagement parts 2a, 2b, 2c of the outer rotor and / or the outer circumference 12 of the engagement parts 3a, 3b of the inner rotor 2 in a gap-forming approach on the inner surface of the machine housing 1.
  • This approximation or the width of these sealing gaps is, depending on the manufacturing quality or depending on the application of the machine or on the density of the medium flowing through the machine, in the order of magnitude of, for example, 0.05 to 0.1 mm.
  • both runners 2, 3 are in drive connection via gear wheels 26, 27, one of which is formed on the inside of the hub-shaped hollow journal 19 by an internal toothing.
  • the gearwheel 28, which is placed on the outside of the shaft journal 15 of the inner rotor 3, is used for driving or driving, depending on whether the machine is driven by a gas flow or promotes it as a compressor.
  • the actual width of the sealing gaps is, for example, 0.05 mm at the narrowest sealing gaps manufactured by manufacture and, for example, 0.1 mm at the widest sealing joints manufactured by manufacture.
  • the sealing gaps D 4 occurring in the area of the radially inner circumferential surfaces 32, 33 of the inner rotor 3 during the rotation of the rotor also have to separate the low and high pressure sides of the machine from one another, but there can be wider sealing gaps D 4 to reduce frictional losses are accepted, since in this area the surfaces of both runners 2, 3 adjacent to the sealing gap are located at a short distance from one another and thus contribute to the sealing, or widen the sealing gap in the circumferential direction.
  • Larger or further sealing gaps on the radially inner circumferential surfaces 32, 33 provide the further advantage of reducing losses due to squeezing currents, in particular when the machine is intended for high rotational speeds of, for example, more than 20,000 rpm.
  • Fig. 4 shows the corresponding embodiment.
  • narrower sealing gaps D 4 are preferably also provided on the radially inner circumferential surfaces 32, 33 of the inner rotor in order to obtain a good seal, as the exemplary embodiment in FIG. 5 shows.
  • the sealing gaps D which occur with respect to the inner surfaces 35,36 of the engagement parts 2a, 2b, 2c are wider in each embodiment according to the invention than in the region of the radial outer peripheral surfaces 12a, 12b, so that the friction losses occurring there are correspondingly low. This is possible without significant sealing losses, since these sealing gaps D i , D 2, in accordance with the representations of the rotational positions in FIGS.
  • the width of the sealing gap Di, D 2 can advantageously be increasingly larger, corresponding to their distance from the axis 5 of the inner rotor, as shown in FIGS. 5 and 6, so that the undersize to be provided for the corresponding sealing gap widths on the inner or outer rotor increases radially outwards.

Claims (5)

1. Machine à piston rotatif à axe interne comportant un rotor externe et un rotor interne, qui sont entourés d'un carter (1) commun, présentant à sa périphérie un canal d'admission (7) et un canal d'échappement (8), et qui sont montés sur paliers, indépendamment l'un de l'autre, autour d'axes géométriquement fixes, tandis que les rotors (2, 3) forment, par leur contact d'engrènement réciproque entre chaque fois deux pièces d'engrènement du rotor externe se suivant l'une derrière l'autre sur la périphérie de ce dernier, des chambres de travail de volume variable qui sont rendus étanches, d'une façon continue, l'une par rapport à l'autre, par le roulement et le glissement, constituant l'interstice d'étanchéité, de zones de surface variables des rotors (2, 3) l'une sur l'autre et sur la surface interne (8) du carter, et tandis que le rotor interne (3) présente, par rapport son axe de rotation, des surfaces extérieures radialement (12a, 12b; 32, 33), ainsi qu'entre elles, une surface intermédiaire (34), caractérisée en ce que les interstices d'étanchéité (D3) entre les deux rotors (2, 3) sur les surfaces extérieures radialement (12a, 12b) du rotor interne (3) sont plus petits que sur leur surfaces intermédiaires (34).
2. Machine à piston rotatif suivant la revendication 1, caractérisée en ce que les interstices d'étanchéité au niveau des surfaces extérieures radialement (12a, 12b) du rotor interne (3) sont plus petites qu'au niveau de ses surfaces intérieures radialement (32, 33; figure 4).
3. Machine à piston rotatif suivant la revendication 1 ou la revendication 2, caractérisée en ce que les interstices d'étanchéité (D4) se produisant au niveau des surfaces intérieures radialement (32, 33) sont plus petites que les interstices d'étanchéité (Ds) se produisant au niveau des surfaces intermédiaires (34) du rotor interne (3).
4. Machine à piston rotatif suivant l'une quelconque des revendications 1 à 3, caractérisée en ce que les interstices d'étanchéité (Ds) se produisant au niveau des surfaces intermédiaires (34) présente une largeur augmentant en allant radialement vers l'extérieur.
5. Machine à piston rotatif suivant l'une quelconque des revendications 1 à 4, caractérisée en ce que les interstices d'étanchéité (D1 à Ds) sont réalisés, sur l'un des rotors (2, 3) ou sur les deux, au moyen d'un écart correspondant en moins par rapport à la forme sans interstice d'étanchéité, dessinée cimématiquement, des rotors.
EP86109613A 1985-08-31 1986-07-14 Machine à piston à axe interne Expired - Lifetime EP0218806B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT86109613T ATE49626T1 (de) 1985-08-31 1986-07-14 Innenachsige drehkolbenmaschine.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH3742/85A CH667492A5 (de) 1985-08-31 1985-08-31 Innenachsige drehkolbenmaschine.
CH3742/85 1985-08-31

Publications (2)

Publication Number Publication Date
EP0218806A1 EP0218806A1 (fr) 1987-04-22
EP0218806B1 true EP0218806B1 (fr) 1990-01-17

Family

ID=4262521

Family Applications (1)

Application Number Title Priority Date Filing Date
EP86109613A Expired - Lifetime EP0218806B1 (fr) 1985-08-31 1986-07-14 Machine à piston à axe interne

Country Status (10)

Country Link
US (1) US4772191A (fr)
EP (1) EP0218806B1 (fr)
JP (1) JPH079161B2 (fr)
KR (1) KR950003057B1 (fr)
AT (1) ATE49626T1 (fr)
BR (1) BR8603853A (fr)
CH (1) CH667492A5 (fr)
DE (1) DE3668345D1 (fr)
ES (1) ES2001514A6 (fr)
MX (1) MX168262B (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2720788B1 (fr) * 1994-06-01 1996-09-20 Barba Willy Del Machine volumétrique réversible à piston(s) rotatif(s) sans clapet à usage de compresseur de fluide de moteur et de pompe à fluide.

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB316295A (en) * 1928-07-27 1930-05-15 Leblanc Vickers Maurice Sa Improvements in or relating to rotary compressors
US3029738A (en) * 1958-09-02 1962-04-17 Borsig Ag Control for rotary piston machines
US3275225A (en) * 1964-04-06 1966-09-27 Midland Ross Corp Fluid compressor
DE2058860C2 (de) * 1970-11-30 1983-02-10 Fürstlich Hohenzollernsche Hüttenverwaltung Laucherthal, 7480 Sigmaringen Rotationskolbenmaschine
DE2456252B2 (de) * 1974-11-28 1977-06-30 Kernforschungsanlage Jülich GmbH, 517OJuIiCh Abdichtungsvorrichtung fuer eine drehkolbenmaschine in trochoidenbauart
DD115184A1 (fr) * 1974-12-04 1975-09-12
GB2104153B (en) * 1981-08-15 1984-08-30 Concentric Pumps Ltd Rotary positive-displacement fluid-pumps
CH664423A5 (de) * 1984-06-12 1988-02-29 Wankel Felix Innenachsige drehkolbenmaschine.

Also Published As

Publication number Publication date
BR8603853A (pt) 1987-03-24
JPH079161B2 (ja) 1995-02-01
CH667492A5 (de) 1988-10-14
MX168262B (es) 1993-05-14
JPS6291602A (ja) 1987-04-27
EP0218806A1 (fr) 1987-04-22
KR870002355A (ko) 1987-03-31
KR950003057B1 (ko) 1995-03-30
US4772191A (en) 1988-09-20
ATE49626T1 (de) 1990-02-15
ES2001514A6 (es) 1988-06-01
DE3668345D1 (de) 1990-02-22

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