EP0218806A1 - Machine à piston à axe interne - Google Patents

Machine à piston à axe interne Download PDF

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Publication number
EP0218806A1
EP0218806A1 EP86109613A EP86109613A EP0218806A1 EP 0218806 A1 EP0218806 A1 EP 0218806A1 EP 86109613 A EP86109613 A EP 86109613A EP 86109613 A EP86109613 A EP 86109613A EP 0218806 A1 EP0218806 A1 EP 0218806A1
Authority
EP
European Patent Office
Prior art keywords
sealing
sealing gaps
rotary piston
piston machine
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.)
Granted
Application number
EP86109613A
Other languages
German (de)
English (en)
Other versions
EP0218806B1 (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
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 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 patent claim 1.
  • 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, in that a good seal between the rotors of the machine is achieved with relatively low 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 D 1, D 2, D 3, D4, D5 ... in sealing gap-forming approach to one another, and along two mutually opposite circumferential regions 10, 11, 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 is in a seal-gap-forming approach to the inner surface of the machine housing 1.
  • This approach or the width of this sealing gap Depending on the manufacturing quality or depending on the application of the machine or on the density of the medium flowing through the machine, it is 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.
  • sealing gaps 4 to 7 is the width of the sealing gaps resulting at the respective sealing points or sealing areas D1 to D5 with a local reference to the inner rotor (Fig. 4, Fig. 5 and Fig. 7) or outer rotor (Fig. 6).
  • dashed lines in large magnification ie schematically represented by the dashed lines giving the size of the inner or outer rotor, in which there would be no sealing gap compared to the other rotor.
  • 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 manufactured sealing points.
  • the smallest sealing gap at the same engagement points D3 between the runners 2,3 results by correspondingly smaller dimensions of the engagement parts 2a, 2b, 2c, as indicated by the solid contour line compared to the dashed contour line of these engagement parts.
  • the distance between the theoretical dashed contour line and the solid contour line is consequently smallest at the radially inner corner regions 30.
  • an undersizing corresponding to the theoretical can be shown in a manner not shown a seal-free contour can also be provided in part on both rotors 2, 3.
  • the in the area of the radially inner circumferential surfaces 32, 33 of the inner rotor 3 during the rotation of the rotor between the two sealing gaps D4 also have to separate the low and high pressure sides of the machine, but wider sealing gaps D4 can be accepted there to reduce frictional losses , since in this area the surfaces of the two runners 2, 3 adjacent to the sealing gap are 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 used for high rotational speeds of e.g. more than 20,000 rpm is provided.
  • Fig. 4 shows the corresponding embodiment.
  • narrower sealing gaps D4 are preferably also provided on the radially inner circumferential surfaces 32, 33 of the inner rotor in order to obtain a good seal, as in the exemplary embodiment in FIG. 5 shows.
  • the sealing gaps D occurring 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 radially 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 1, D 2 only occur in accordance with the representations of the rotational positions in FIGS. 3a to 3l if the radially outer peripheral surfaces 12a, 12b are in sealing proximity to the peripheral regions 10, 11 of the housing inner surface, so they don't have to seal the low pressure side from the high pressure side of the machine alone.
  • a better sealing effect is present anyway on these transition surfaces due to their tooth-flank-like engagement with the inner surfaces 35, 36 and the correspondingly flatter sealing-gap-forming surfaces tapering in the direction of the pressure gradient.
  • the width of the sealing gap D 1, 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 for the corresponding sealing gap widths on the inner or outer runner undersize to be provided increases radially outwards.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Soil Working Implements (AREA)
  • Friction Gearing (AREA)
  • Motorcycle And Bicycle Frame (AREA)
  • Centrifugal Separators (AREA)
  • Steroid Compounds (AREA)
  • Toys (AREA)
  • X-Ray Techniques (AREA)
  • Vehicle Body Suspensions (AREA)
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 true EP0218806A1 (fr) 1987-04-22
EP0218806B1 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)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1995033126A1 (fr) * 1994-06-01 1995-12-07 Willy Del Barba Machine volumetrique a piston rotatif

Citations (3)

* 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
DE2552454A1 (de) * 1974-12-04 1976-06-10 Sasnowski Hydraulik Nord Drehkolbenmaschine, vorzugsweise fuer fluessigkeiten
EP0072636A2 (fr) * 1981-08-15 1983-02-23 Concentric Pumps Limited Pompes rotatives à fluide à N/N +1 lobes

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
CH664423A5 (de) * 1984-06-12 1988-02-29 Wankel Felix Innenachsige drehkolbenmaschine.

Patent Citations (3)

* 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
DE2552454A1 (de) * 1974-12-04 1976-06-10 Sasnowski Hydraulik Nord Drehkolbenmaschine, vorzugsweise fuer fluessigkeiten
EP0072636A2 (fr) * 1981-08-15 1983-02-23 Concentric Pumps Limited Pompes rotatives à fluide à N/N +1 lobes

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1995033126A1 (fr) * 1994-06-01 1995-12-07 Willy Del Barba Machine volumetrique a piston rotatif
FR2720788A1 (fr) * 1994-06-01 1995-12-08 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.

Also Published As

Publication number Publication date
ATE49626T1 (de) 1990-02-15
JPH079161B2 (ja) 1995-02-01
DE3668345D1 (de) 1990-02-22
JPS6291602A (ja) 1987-04-27
US4772191A (en) 1988-09-20
KR870002355A (ko) 1987-03-31
KR950003057B1 (ko) 1995-03-30
MX168262B (es) 1993-05-14
ES2001514A6 (es) 1988-06-01
CH667492A5 (de) 1988-10-14
EP0218806B1 (fr) 1990-01-17
BR8603853A (pt) 1987-03-24

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