EP0167846A1 - Machine à piston rotatif à axe interne - Google Patents

Machine à piston rotatif à axe interne Download PDF

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Publication number
EP0167846A1
EP0167846A1 EP85107098A EP85107098A EP0167846A1 EP 0167846 A1 EP0167846 A1 EP 0167846A1 EP 85107098 A EP85107098 A EP 85107098A EP 85107098 A EP85107098 A EP 85107098A EP 0167846 A1 EP0167846 A1 EP 0167846A1
Authority
EP
European Patent Office
Prior art keywords
rotor
outer rotor
rotary piston
piston machine
machine according
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
EP85107098A
Other languages
German (de)
English (en)
Other versions
EP0167846B1 (fr
Inventor
Felix Dr. H.C. Wankel
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 AT85107098T priority Critical patent/ATE51432T1/de
Publication of EP0167846A1 publication Critical patent/EP0167846A1/fr
Application granted granted Critical
Publication of EP0167846B1 publication Critical patent/EP0167846B1/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
    • F01C20/00—Control of, monitoring of, or safety arrangements for, machines or engines
    • F01C20/10—Control of, monitoring of, or safety arrangements for, machines or engines characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
    • F01C20/14—Control of, monitoring of, or safety arrangements for, machines or engines characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using rotating valves
    • 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 with the features of the preamble of claim 1.
  • the invention has for its object to find an improved machine of the type mentioned, which, due to the shape of its rotor, has a higher throughput, based on its construction volume, and very small, harmful spaces and thereby enables high rotation speeds of its rotor.
  • the invention results in a cross-sectional shape of the rotor, which enables high rotational speeds, although the inner rotor can move up to the outer circumference of the outer rotor or even beyond in order to achieve very small, harmful spaces.
  • the machine according to the invention has surprisingly large working spaces in relation to the overall dimensions of the machine.
  • the side surfaces of the outer rotor that delimit the inner working spaces are preferably designed to be flat, wherein opposite inner side surfaces can advantageously run parallel to one another, so that large cross sections of the working spaces and large control openings on the outer rotor result.
  • outer corner areas of the inner rotor and the inner corner areas of the outer rotor are advantageous with con constant or variable cross-sectional curvature rounded.
  • the inner corner areas of the outer rotor are guided radially inwards so that they come close to the shaft.
  • the gear ratio between the inner and outer rotor is 2: 1, 3: 2, 4: 3, etc.
  • At least one adjustable wall piece which is provided on the inside of the housing and along which the circumference of the outer rotor moves, enables the delivery rate and / or the delivery pressure to be controlled by changing the time of inflow and thus the Size of the filling and / or the time of the outflow and thus the pressure level of the overflow in the pressure line changed.
  • a machine according to the invention can also be an internal combustion engine.
  • the cross-sectional view shows three main parts of the machine, i.e. an inner rotor 1, an outer rotor 2, with three rigidly connected rotor parts 2a, 2b and 2c and the housing 3 enclosing both of them.
  • the cross-sectional illustration in FIG visible boundary surfaces of these parts parallel to the axes of rotation of the rotor, while their invisible end boundary surfaces are perpendicular to these axes.
  • the wall of the housing 3 merges into an inflow and outflow channel 4, 5, it depending on the use of the machine whether the inflow channel 4 is an intake channel or an inflow channel for a propellant.
  • Both runners 1, 2 rotate about fixed axes 6, 7 which are at a distance from one another.
  • the speed ratio is 3: 2, corresponding to the ratio between the number of cutouts 8, 9, 10 forming the work spaces of the outer rotor to the number of parts 11, 12 of the inner rotor that extend away from the axis 6.
  • this ratio is 4: 3, corresponding to four recesses 14, 15, 16, 17 and three parts 18, 19, 20 of the inner rotor that move into and out of the recesses.
  • the movement sequence of the two runners 1, 2 relative to one another and relative to the machine housing 3 can be seen in the illustrations in FIG. 3.
  • the uninterrupted sealing between the inner and outer rotor results from the fact that both runners mutually create their shape when they move relative to each other.
  • the four outer corner regions 20-25 of the inner rotor according to FIG. 1 and the three inner corner regions 26, 27, 29 of the outer rotor are used for generating curves.
  • the corner regions of the inner rotor move or produce along the inner side surfaces 30, 31 of the outer rotor, and the inner corner regions 26, 27, 28 of the outer rotor move along or on the outer peripheral surfaces 32, 33 of the inner rotor generate these. This is illustrated by the movement positions shown in FIG. 3.
  • the seal between the inner side surfaces 30, 31 of the outer rotor and the side surfaces 34, 35 of the inner rotor results from a tooth flank-like contact between the two.
  • the corner areas 22 - 28 of both runners are preferably rounded instead of sharp-edged, so that the rounding on the other rotor creates an equidistant from the center of curvature of the rounding.
  • the inner corner region 28 of the outer rotor 2 is relatively close to the axis of the inner rotor, as a comparison with the prior art according to the aforementioned DE-OS 2 456 252 shows.
  • the throughput volume is, for example, 1 dm 3 .
  • the inner side surfaces 30, 31 of the outer rotor run parallel to one another, so that the opening of the recesses 8, 9, 10 of the outer rotor, which moves past the housing openings at a very high speed, is correspondingly advantageously large.
  • this opening cross section of the cutouts of the outer rotor is advantageously large.
  • the exemplary embodiment according to FIG. 7 shows inner side surfaces of the outer rotor which run slightly towards one another radially outward.
  • the outer circumferential surfaces 32, 33 of the inner rotor move up to the outer circumference of the outer rotor, so that the harmful space results due to the different curvature of the circumferential surface of the inner rotor and the circumferential surface of the outer rotor. Since the outer peripheral surfaces 32, 33 of the inner rotor can also take over the sealing alone when passing through the sealing area 42 between the two channels 4, 5 of the housing, it is possible that these peripheral surfaces 32, 33 also move beyond the circumference of the outer rotor.
  • a wall piece 43 which is adjustable in the circumferential direction, so that the internal compression of the machine can be changed starting from zero.
  • Fig. 1 shows a position of the wall piece 43, through which there is no internal compression, while in the position according to Fig. 2, the internal compression takes place until the rotational position shown, until the working space 8 opens by the trailing edge 44 of the outer rotor away from the wall piece 43.
  • an actuating member not shown, which extends outwards through a slot in the housing wall.
  • the throughput can also be changed, since in this way the angular range of the rotation of the external rotor is reduced, within the medium of which in the increasingly larger working space 8 can flow between the two runners.
  • Fig. 4 shows another embodiment for the design of means for changing the throughput volume and / or the internal compression of the machine.
  • These means consist of a plurality of circular arc-shaped radial slides 46, 47 arranged next to one another in the circumferential direction on the inflow and outflow side of the machine in the direction of rotation of the rotors in the direction of arrow 48.
  • the inflow-side radial slides change the size of the arc region adjoining the inflow channel 4 ′, via the an inflow in both runners enclosed work space 8 'in the direction of arrow 49.
  • FIG. 4 shows two inflow-side radial slides 46 in the radially outer position, while the radial slides adjoining in the direction of rotation have their radially innermost position, so that maximum internal compression is achieved when the machine is operated as a compressor.
  • the strength of the internal compression can be gradually changed in this exemplary embodiment according to FIG. 4, corresponding to the number of radial slides 47 which are retracted radially outward from the position shown.
  • this means 43, 46, 47 for changing the delivery rate and / or the internal compression can be used on any machine in which there is an outer rotor rotating about a fixed axis, the recesses of which form radially outwardly open working spaces move past housing openings.
  • FIG. 6 shows how a machine according to the invention according to FIG. 7 can look in the axial cross section.
  • the parts of the machine according to FIGS. 6 and 7 already described with reference to FIG. 1 have the same reference numbers.
  • the parts 2a, 2b, 2c of the outer rotor are rigidly connected to one another at the two axial ends of the rotor by side plates 50, 51.
  • a hub 52 or 53 projects axially outward from these side plates, via which the outer rotor is mounted on the housing side plates 56, 57 by means of a ball bearing 54 or 55 of large diameter.
  • the hub 53 of the outer rotor has an internal toothing 58 which meshes with a gearwheel 60 fastened on the shaft journal 59 of the inner rotor 1.
  • This drive connection which is thus present, is recommended for an exact run of the two runners to one another, so that there is always an optimal gap seal between the two runners, although the tooth-flank-like contact between the side surfaces of both runners could make the additional gear connection 58, 60 superfluous.
  • the side plates 50, 51 of the outer rotor enclose circular lateral sealing plates 62, 63 which are screwed onto the housing sides 56, 57 and adjoin the end surfaces 64, 65 of the inner rotor with a sealing gap distance.
  • These sealing plates also enclose the two shaft journals 59, 66 of the inner rotor.
  • the outer bearing 44 of the outer rotor also encloses the rolling bearing 67, 68 which supports the shaft journals 59, 66.
  • the gearwheel 69 which laterally projects beyond the housing plate 70 and is attached to the shaft journal 59 of the inner rotor, serves either to drive the machine when it is used as a blower or compressor or as an output gear when the machine is driven as a motor or driver by an inflowing medium, such as the exhaust gas of an internal combustion engine.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
  • Rotary Pumps (AREA)
  • Toys (AREA)
  • X-Ray Techniques (AREA)
  • Steroid Compounds (AREA)
  • Formation And Processing Of Food Products (AREA)
  • Yarns And Mechanical Finishing Of Yarns Or Ropes (AREA)
  • Confectionery (AREA)
EP85107098A 1984-06-12 1985-06-08 Machine à piston rotatif à axe interne Expired - Lifetime EP0167846B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT85107098T ATE51432T1 (de) 1984-06-12 1985-06-08 Innenachsige drehkolbenmaschine.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH2822/84 1984-06-12
CH2822/84A CH664423A5 (de) 1984-06-12 1984-06-12 Innenachsige drehkolbenmaschine.

Publications (2)

Publication Number Publication Date
EP0167846A1 true EP0167846A1 (fr) 1986-01-15
EP0167846B1 EP0167846B1 (fr) 1990-03-28

Family

ID=4242370

Family Applications (1)

Application Number Title Priority Date Filing Date
EP85107098A Expired - Lifetime EP0167846B1 (fr) 1984-06-12 1985-06-08 Machine à piston rotatif à axe interne

Country Status (6)

Country Link
US (2) US4714417A (fr)
EP (1) EP0167846B1 (fr)
JP (1) JPH0612045B2 (fr)
AT (1) ATE51432T1 (fr)
CH (1) CH664423A5 (fr)
DE (2) DE3432915C2 (fr)

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3717346A1 (de) * 1987-05-22 1988-10-13 Daimler Benz Ag Innenachsige drehkolbenmaschine
EP0337950A2 (fr) * 1988-04-15 1989-10-18 Renz, Gerhard Moteur à piston rotatif à axe interne
FR2634820A1 (fr) * 1988-07-27 1990-02-02 Pierburg Gmbh Machine a piston rotatif
EP0568493A2 (fr) * 1992-04-01 1993-11-03 TES WANKEL, TECHNISCHE FORSCHUNGS- UND ENTWICKLUNGSSTELLE LINDAU GmbH Machine à piston rotatif à axe interne

Families Citing this family (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CH664423A5 (de) * 1984-06-12 1988-02-29 Wankel Felix Innenachsige drehkolbenmaschine.
CH667492A5 (de) * 1985-08-31 1988-10-14 Wankel Felix Innenachsige drehkolbenmaschine.
CH669975A5 (fr) * 1986-06-13 1989-04-28 Wankel Felix
FR2603944A1 (fr) * 1986-09-17 1988-03-18 Pierburg Gmbh Dispositif pour commander un moteur a piston rotatif
DE3631574C1 (en) * 1986-09-17 1988-02-25 Pierburg Gmbh Device for controlling a rotary engine
DE3702558A1 (de) * 1987-01-29 1988-09-01 Pierburg Gmbh Innenachsige drehkolbenmaschine
DE3706588C2 (de) * 1987-02-26 1993-12-02 Mannesmann Ag Antriebseinrichtung für Rotationskolbenverdichter
JPS63243482A (ja) * 1987-03-31 1988-10-11 Aisin Seiki Co Ltd 回転ロ−タ装置
DE3716083A1 (de) * 1987-05-14 1988-11-24 Kuehnle Kopp Kausch Ag Innenachsige drehkolbenmaschine
US4948352A (en) * 1987-09-25 1990-08-14 Aisin Seiki Kabushiki Kaisha Rotor unit with peripheral projections and clearances for centrifugal deflection
JPS6483801A (en) * 1987-09-25 1989-03-29 Aisin Seiki Rotor device
JPH0192595A (ja) * 1987-09-30 1989-04-11 Aisin Seiki Co Ltd 回転ロータ装置
DE3817318C2 (de) * 1988-05-20 1997-05-28 Mueller Alander Gerd Dipl Ing Hubkolben-Brennkraftmaschine mit wenigstens einem Drehkolben-Lader der Verdrängerbauart
US5046932A (en) * 1989-11-17 1991-09-10 Compression Technologies, Inc. Rotary epitrochoidal compressor
CH682939A5 (de) * 1990-03-09 1993-12-15 Voith Gmbh J M Innenzahnradpumpe.
CH682587A5 (de) * 1990-12-28 1993-10-15 Gerhard Renz Fried Meysen Thom Rotationskolbenmaschine.
CH689427A5 (de) * 1991-07-09 1999-04-15 Daimler Benz Ag Abdichtung an einem rotierenden Koerper.
EP0563661A1 (fr) * 1992-03-19 1993-10-06 J.M. Voith GmbH Pompe à engrenages internes avec des éléments d'étanchéité mobiles radialement pour la compensation radiale
US7726959B2 (en) * 1998-07-31 2010-06-01 The Texas A&M University Gerotor apparatus for a quasi-isothermal Brayton cycle engine
US6427453B1 (en) * 1998-07-31 2002-08-06 The Texas A&M University System Vapor-compression evaporative air conditioning systems and components
US7186101B2 (en) * 1998-07-31 2007-03-06 The Texas A&M University System Gerotor apparatus for a quasi-isothermal Brayton cycle Engine
US6273695B1 (en) 1999-03-26 2001-08-14 Voith Turbo Gmbh & Co. Kg Sickleless internal gear wheel pump with sealing elements inserted into the tooth tips
CA2385184A1 (fr) * 1999-09-20 2001-03-29 Edward H. Gervais Ensemble de rotors a generation de champ interne pour applications de dosage de fluides abrasifs et de fluides a faible viscosite
US6465645B1 (en) * 2001-04-17 2002-10-15 Ciba Specialty Chemicals Corporation Long chain hindered amines and compositions stabilized therewith
US20100003152A1 (en) * 2004-01-23 2010-01-07 The Texas A&M University System Gerotor apparatus for a quasi-isothermal brayton cycle engine
EP1472434A2 (fr) * 2002-02-05 2004-11-03 The Texas A & M University System Appareil a rotor dente pour moteur a cycle de brayton quasi isotherme
US7663283B2 (en) * 2003-02-05 2010-02-16 The Texas A & M University System Electric machine having a high-torque switched reluctance motor
JP4366197B2 (ja) * 2004-01-21 2009-11-18 Ｈｏｙａ株式会社 ステージ装置及びこのステージ装置を利用したカメラの手振れ補正装置
EP1802858A4 (fr) * 2004-10-22 2010-03-17 Texas A & M Univ Sys Dispositif de pompe a rotor pour moteur a cycle de brayton quasi-isothermique
US7281513B1 (en) 2006-02-24 2007-10-16 Webb David W Inverted Wankel
EP4295046A1 (fr) 2021-02-19 2023-12-27 1158992 B.C. Ltd. Dispositif de transfert de fluide

Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB394985A (en) * 1932-01-05 1933-07-05 Hugo Grasse Improvements in rotary pumps, blowers and motors, and in machines for use in producing the rotors thereof
US2442254A (en) * 1943-03-27 1948-05-25 Joseph E Whitfield Composite metal article
US2701683A (en) * 1951-12-15 1955-02-08 Read Standard Corp Interengaging rotor blower
FR1136949A (fr) * 1954-10-29 1957-05-21 Borsig Ag Dispositif pour le réglage du rendement d'un compresseur à pistons tournants
GB839193A (en) * 1955-06-28 1960-06-29 Edward Gordon Thomas Improvements in or relating to geared mechanism
FR1252836A (fr) * 1959-12-24 1961-02-03 Renault Machine à chambres rotatives
GB1046504A (en) * 1962-06-06 1966-10-26 William Hayter Rotary piston internal combustion engines or pumps
DE1551128A1 (de) * 1966-08-22 1970-02-12 Link Edwin A Drehkolbenanordnung

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US3118387A (en) * 1964-01-21 Reveksible gear pump
US1341846A (en) * 1918-04-22 1920-06-01 Ellick H Gollings Rotary power device
US1292091A (en) * 1918-09-06 1919-01-21 James O Schirmer Fluid transmission or driving mechanism.
US1970146A (en) * 1926-03-01 1934-08-14 Myron F Hill Reversible liquid pump
US1753476A (en) * 1927-06-29 1930-04-08 Joseph R Richer Rotary pump or blower
DE556181C (de) * 1930-03-18 1932-08-09 Hugo Grasse Zahnradmaschine mit Inneneingriff, insbesondere als Geblaese
US2601397A (en) * 1950-04-11 1952-06-24 Hill Myron Francis Rotary fluid displacement device
DE1015572B (de) * 1954-10-29 1957-09-12 Borsig Ag Vorrichtung zum Regeln der Foerderleistung von Drehkolbenverdichtern
US2956506A (en) * 1955-11-21 1960-10-18 Robert W Brundage Hydraulic pump or motor
US2965039A (en) * 1957-03-31 1960-12-20 Morita Yoshinori Gear pump
US3029738A (en) * 1958-09-02 1962-04-17 Borsig Ag Control for rotary piston machines
US3108739A (en) * 1960-06-17 1963-10-29 Svenska Rotor Maskiner Ab Regulating means for rotary piston compressor
US3151806A (en) * 1962-09-24 1964-10-06 Joseph E Whitfield Screw type compressor having variable volume and adjustable compression
DE1264866B (de) * 1964-08-11 1968-03-28 Eugen Wilhelm Huber Dr Ing Heissgas-Drehkolbenmaschine
DE2456252B2 (de) * 1974-11-28 1977-06-30 Kernforschungsanlage Jülich GmbH, 517OJuIiCh Abdichtungsvorrichtung fuer eine drehkolbenmaschine in trochoidenbauart
SU652335A1 (ru) * 1977-06-09 1979-03-15 Всесоюзный Научно-Исследовательский И Проектный Институт По Переработке Газа Роторна машина
SU673745A1 (ru) * 1977-11-22 1979-07-15 Московское Ордена Ленина И Ордена Трудового Красного Знамени Высшее Техническое Училище Им. Н.Э.Баумана Роторна машина
JPS5660801A (en) * 1979-10-20 1981-05-26 Kawasaki Heavy Ind Ltd Rotary fluid machine
CH664423A5 (de) * 1984-06-12 1988-02-29 Wankel Felix Innenachsige drehkolbenmaschine.
DE3528502A1 (de) * 1985-08-08 1987-02-19 Pierburg Gmbh & Co Kg Vorrichtung zum steuern einer drehkolbenmaschine

Patent Citations (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB394985A (en) * 1932-01-05 1933-07-05 Hugo Grasse Improvements in rotary pumps, blowers and motors, and in machines for use in producing the rotors thereof
US2442254A (en) * 1943-03-27 1948-05-25 Joseph E Whitfield Composite metal article
US2701683A (en) * 1951-12-15 1955-02-08 Read Standard Corp Interengaging rotor blower
FR1136949A (fr) * 1954-10-29 1957-05-21 Borsig Ag Dispositif pour le réglage du rendement d'un compresseur à pistons tournants
GB839193A (en) * 1955-06-28 1960-06-29 Edward Gordon Thomas Improvements in or relating to geared mechanism
FR1252836A (fr) * 1959-12-24 1961-02-03 Renault Machine à chambres rotatives
GB1046504A (en) * 1962-06-06 1966-10-26 William Hayter Rotary piston internal combustion engines or pumps
DE1551128A1 (de) * 1966-08-22 1970-02-12 Link Edwin A Drehkolbenanordnung

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3717346A1 (de) * 1987-05-22 1988-10-13 Daimler Benz Ag Innenachsige drehkolbenmaschine
EP0337950A2 (fr) * 1988-04-15 1989-10-18 Renz, Gerhard Moteur à piston rotatif à axe interne
EP0337950A3 (en) * 1988-04-15 1990-02-28 Renz, Gerhard Internal axis rotary piston engine
FR2634820A1 (fr) * 1988-07-27 1990-02-02 Pierburg Gmbh Machine a piston rotatif
EP0568493A2 (fr) * 1992-04-01 1993-11-03 TES WANKEL, TECHNISCHE FORSCHUNGS- UND ENTWICKLUNGSSTELLE LINDAU GmbH Machine à piston rotatif à axe interne
EP0568493A3 (en) * 1992-04-01 1993-12-15 Lindau Tech Forsch & Entw Gmbh Internal axis rotary piston machine

Also Published As

Publication number Publication date
JPH0612045B2 (ja) 1994-02-16
EP0167846B1 (fr) 1990-03-28
DE3432915A1 (de) 1985-12-12
CH664423A5 (de) 1988-02-29
US4801255A (en) 1989-01-31
DE3576839D1 (de) 1990-05-03
JPS614802A (ja) 1986-01-10
ATE51432T1 (de) 1990-04-15
DE3432915C2 (de) 1987-01-02
US4714417A (en) 1987-12-22

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