EP0088288A1 - Machine à piston rotatif à axe interne - Google Patents

Machine à piston rotatif à axe interne Download PDF

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Publication number
EP0088288A1
EP0088288A1 EP83101744A EP83101744A EP0088288A1 EP 0088288 A1 EP0088288 A1 EP 0088288A1 EP 83101744 A EP83101744 A EP 83101744A EP 83101744 A EP83101744 A EP 83101744A EP 0088288 A1 EP0088288 A1 EP 0088288A1
Authority
EP
European Patent Office
Prior art keywords
rotor
shut
piston
wall
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.)
Withdrawn
Application number
EP83101744A
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German (de)
English (en)
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
Priority claimed from CH1302/82A external-priority patent/CH664193A5/de
Application filed by Individual filed Critical Individual
Publication of EP0088288A1 publication Critical patent/EP0088288A1/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Withdrawn legal-status Critical Current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
    • F01C21/00—Component parts, details or accessories not provided for in groups F01C1/00 - F01C20/00
    • F01C21/02—Arrangements of bearings
    • 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
    • F01C1/30—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members
    • F01C1/36—Rotary-piston machines or engines having the characteristics covered by two or more groups F01C1/02, F01C1/08, F01C1/22, F01C1/24 or having the characteristics covered by one of these groups together with some other type of movement between co-operating members having both the movements defined in sub-groups F01C1/22 and F01C1/24

Definitions

  • the invention relates to an internal-axis crankshaft-less rotary piston machine with a piston rotor, the at least one piston of which moves through a circular annular space with a fixed inner wall and a gap of a shut-off rotor, which blocks the annular space at one point on its circumference.
  • a rotary piston machine of the type mentioned is known from DE-PS 180927 from 1905.
  • the propellant is fed through narrow channels in the side walls of the machine and flows freely outwards via narrow channels in the piston and a rotating closed cylinder.
  • the drive connection between the piston rotor and the shut-off Runner occurs through frictional contact between the two.
  • the present invention is based on the object of finding a machine which is particularly suitable as a driver and loader of an internal combustion engine and which combines the advantages of a turbo machine with those of a rotary piston machine in that it is suitable for high throughput quantities in a small size and is also more efficient than these machines due to lower flow losses and fewer harmful rooms.
  • the solution to this problem is that in the case of a rotary piston machine of the type mentioned at the outset, the inflow channel opens into the annular space via an opening in the fixed inner wall or is arranged adjacent to the shut-off rotor in a fixed radially outer housing wall and that the outflow channel adjoins the shut-off rotor in a fixed radially outer housing wall is provided.
  • the arrangement of the inflow channel in the fixed inner wall of the ring channel is particularly advantageous when the machine is to be used as a loader or compressor, since a centrifugal machine-like flow is achieved through the machine and its ring channel.
  • the feed opening can be made particularly wide in the circumferential direction. In the axial direction, the openings of the channels into the annular channel can correspond at least approximately to the axial length of the pistons. Since the machine can be very long in relation to its diameter in the axial direction, correspondingly long openings can result, so that low flow resistances occur when flowing through the machine.
  • the shut-off rotor has an effective outer diameter which is half the outer diameter of the outer rotor twice the speed of rotation of the gate rotor compared to the piston rotor, so that due to this special kinematics, the two mutually opposite opening edges of the recess provided in the gate rotor can be provided in constant sealing contact with the piston during the passage of a piston. In this way it can be prevented that the propellant or the conveyed medium from the inflow side to the outflow side of the machine or vice versa passes through the cutout or the shut-off rotor.
  • shut-off rotor Due to the so-called inner-axis arrangement of the shut-off rotor relative to the piston runner in accordance with the terminology mentioned in the aforementioned specialist book, a common flow-shaped cross-sectional shape results between the shut-off rotor and the inner wall of the ring channel, which is approximately egg-shaped.
  • a flow-efficient guidance of the propellant or of the conveyed medium through the machine results from the fact that the at least one flow channel provided on the outer housing wall is directed tangentially to the outer circumference of the shut-off rotor and the inner wall of the ring channel.
  • the rotary piston machine according to the invention is designed without a crankshaft, i.e. it is a so-called rotary piston machine instead of a rotary piston machine, and the rotors thus rotate about fixed geometric axes, the rotors can work at very high speeds of rotation, however no suitable means were previously known for the selected inner-axis
  • the bearing of the outer rotor must enclose that of the inner rotor at its two axial ends when the rotor is mounted.
  • this difficulty was circumvented by the fact that the shut-off rotor had no bearings at its two axial ends, ie bearing journals or the like. has, but on one Part of its circumference is enclosed by an arcuate recess in the fixed housing. Accordingly, the drive transmission between the two runners had to be carried out by passing them on to one another with frictional contact.
  • the outer rotor with at least one circularly curved raceway which surrounds the shaft of the shut-off rotor and is supported by a plurality of bearing devices which are spaced apart from one another in the running direction and preferably consist of a roller and which are fixed to a common body are.
  • This common body can be firmly connected to the stationary outer housing and extend into the space enclosed by the raceway, so that it can also serve to support the shaft of the shut-off rotor.
  • the arrangement of the shaft of the shut-off rotor can be provided between them by using individual bearing devices in the circumferential direction.
  • the use of a conventional plain or roller bearing with a diameter corresponding to the mentioned track would not be expedient due to the high sliding or rolling speeds.
  • the use of rollers as bearing devices enables higher rotational speeds with less frictional resistance.
  • the driver with the rotational positions corresponding to the representations according to FIGS. La-lf has a fixed outer housing 1 and a fixed inner housing 2, between which a piston rotor 3 and a shut-off rotor 4 are enclosed.
  • the outer housing 1, the wall of the inner housing 2, the ring channel 5 enclosed between the two and the piston rotor 3 have the same geometric axis, so that the pistons 6, 7 are in sealing contact with the outer and inner housings 1, 2 through the annular space 5 move.
  • the direction of rotation and conveyance is indicated by arrow 8.
  • the medium to be pumped which is air when using the machine as a loader of an internal combustion engine, is via the inner housing 2 from the outside of the machine sucked in via inlet openings 9 and then conveyed radially outward into the annular channel 5 via the opening 10 in the inner wall of the housing in the manner of a centrifugal fan.
  • the lateral arrangement of the inlet openings 9 can be seen from the axial sectional view in FIG. 6, which corresponds both to the exemplary embodiment according to FIGS. 1 a to 11 and to that according to FIG. 5.
  • the opening 10 in the inner wall of the housing extends in the axial direction as much as possible over the largest part of the axial length of the machine, as can be seen in the illustration in FIG. 6, and also has a considerable width in the circumferential direction, starting from the circumference of the shut-off rotor 4 up to a rotational position of the piston 6 as shown in FIG. 1f, in which the diametrically opposed second piston 7 has just passed the outlet channel 12, so that at this moment the compression can begin in the blocked-off part 5a of the annular space.
  • FIGS. 1 a - lf show how the cylindrical peripheral part of the piston rotor 3 opens and closes the outflow channel 12. In the open position, one of the rotor openings 14, 15 arranged in front of the pistons faces the outlet channel 12, as shown in FIG.
  • the piston 7 penetrates into the cutout 16 of the shut-off rotor 4 at the moment when the leading side edge 17 of the cutout loses sealing contact with the concave, circular inner housing wall 18.
  • the piston 7 penetrates into the recess 16 s o that it can not open to the annular space 5 towards.
  • this leading edge 17 of the shut-off rotor 4 slides along the flat front side surface of the piston, while the trailing edge 19 of the recess on the rear flat surface Side surface of the piston slides along.
  • the flat side surfaces of the piston are possible due to the kinematics given by the diameter and speed ratio of 2: 1 between the diameter of the shut-off rotor 4 and the inner diameter of the piston rotor 3, since with a relative rolling movement of the inner circle there is a point in an outer circle of twice the diameter of the inner circle moved on a straight line relative to the outer circle.
  • La-lf the opening edges 17, 19 of the recess 16 of the shut-off rotor 4 are shown with sharp edges, but to reduce the wear of these edges they are advantageously rounded, for example in accordance with the exemplary embodiments of FIGS. 7 and 8 is the center of the rounding of these edges 17 1 , 19 ', 17 ", 19" at the intersection between the pitch circle 20 and an equidistant 21 at a distance from the radius of curvature to the piston side surface 22.
  • the gap between the edges 17, 19 of the cutout 16 of the gate valve corresponds to a tooth gap of a ring gear for the engagement of the teeth or the pistons of the piston rotor comparable to a hollow gear.
  • a cutout would in itself be sufficient, which is precisely adapted to the size of the piston and the required movement space of the piston, like the cutout 16 shown in the exemplary embodiment in FIGS however, is only in the flat side walls of the gate valve, of which only the side wall 23 is visible in the illustrations.
  • the shut-off rotor is provided with an escape space 25. In the illustrated embodiment, this has a maximum size in that the shut-off rotor is designed as a hollow cylinder.
  • FIG. 5 shows a special form of drive transmission between a piston rotor 3 'and a shut-off rotor 4', in that the circular-cylindrical wall of the piston rotor is provided with an internal toothing 27 and the shut-off rotor 4 'with an external toothing 28, of which to simplify the illustration in FIG Fig. 5 only one arc area is shown. In the engagement area, the meshing results in a labyrinth-like seal between the two runners.
  • the machine according to FIG. 5 as a loader can be directly coupled to the machine according to FIG. 2 as a driver of an internal combustion engine, in that the shut-off rotor and the piston rotor are rigidly connected to one another.
  • a drive transmission between the piston rotor and the shut-off rotor can also take place directly by the engagement of the pistons in the cutouts (tooth gaps) of the shut-off rotor if the piston rotor is provided with eight pistons and the shut-off rotor is provided with four recesses.
  • 3 shows a piston rotor with four on the embodiment of a driver Pistons 30-33 and a shut-off valve with two recesses 34, 35.
  • the inflow channel 36 and the outflow channel 37 are for the driving medium, e.g. the exhaust gas of an internal combustion engine, arranged tangentially on the outer housing 38 on both sides of the shut-off rotor 39, in such a way that the inflow and outflow occur tangentially to the outer surface of the shut-off rotor 39 and to the circular-cylindrical inner wall 40 of the housing, as indicated by the broken lines 41, 42 in FIG. 2 is.
  • the ring channel 44 for driving the pistons 45, 46 of the piston rotor.
  • the shut-off rotor 39 has a somewhat larger diameter than half the inner diameter of the housing outer wall 38, so that the shut-off rotor is in contact with the housing along an arcuate line 48 and there is a larger sealing surface between the two. Nevertheless, a diameter ratio of 2: 1 is achieved in contact with the piston of the piston rotor, since the contact is made on a correspondingly smaller diameter by rounding the opening edges 50, 51 of the shut-off rotor 39.
  • the piston rotor 3 "has two circular side walls 52, 53, the inner ring surfaces 54, 55 of which form a bearing raceway, which is supported by three rollers 56, 57, 58 and 56 ', 57', 58 ', which are arranged at the same distance from one another in the circumferential direction
  • the bearings or journals 60, 61 of these rollers are held in a housing part 62, 63, which is secured by screws 64, 65 to the housing side plates 66, 67 is bound and extends into the space enclosed by the raceway 54, 55.
  • the shaft 68 of the shut-off rotor can be arranged in the circumferential direction between two of these rollers 57, 58, as shown in the illustration in FIG. 9.
  • the use of the rollers 56-58 for the bearing of the outer rotor also leads to a significantly reduced bearing friction in comparison to conventional roller bearings and thus enables higher speeds of rotation of the rotor.
  • the fixed housing part 62, 63, which receives the rollers 56-58, can also have flow channels 70, 71, 72, through which a connection to the cavity 73 of the inner housing can take place, for example for cooling purposes. 4 and 6, a portion of the intake air of the charger according to FIG. 6 can flow through these channels 70-72 in a manner not shown, which in the main flow via the side supports 74 (FIG. 6 ) is supplied.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Supercharger (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
EP83101744A 1982-03-03 1983-02-23 Machine à piston rotatif à axe interne Withdrawn EP0088288A1 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
CH1302/82 1982-03-03
CH1302/82A CH664193A5 (de) 1982-03-03 1982-03-03 Abgasbetriebener rotationskolbenlader.
CH670882 1982-11-17
CH6708/82 1982-11-17

Publications (1)

Publication Number Publication Date
EP0088288A1 true EP0088288A1 (fr) 1983-09-14

Family

ID=25687256

Family Applications (1)

Application Number Title Priority Date Filing Date
EP83101744A Withdrawn EP0088288A1 (fr) 1982-03-03 1983-02-23 Machine à piston rotatif à axe interne

Country Status (2)

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US (1) US4490101A (fr)
EP (1) EP0088288A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0137421A2 (fr) * 1983-10-10 1985-04-17 Wankel, Felix, Dr. h.c. Machine à piston rotatif à axe externe

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6484687B1 (en) * 2001-05-07 2002-11-26 Saddle Rock Technologies Llc Rotary machine and thermal cycle
US20060156711A1 (en) * 2005-01-20 2006-07-20 Carpenter Todd L Internal combustion engine with secondary air pump for catalyst
US9127548B2 (en) * 2011-03-23 2015-09-08 Arthur Ryuji Ishii 3-stroke/6-stroke rocket jet engine
CN103233782B (zh) * 2012-09-07 2015-09-09 胡武琼 旋塞式旋转压缩膨胀机构
EP2762675A1 (fr) 2013-02-03 2014-08-06 Cornel Ciupan Moteur rotatif a combustion interne

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE225311C (fr) *
DE156261C (fr) *
US1408839A (en) * 1920-11-29 1922-03-07 Sparrow Charles Mck Rotary pump and engine
GB245277A (en) * 1925-01-14 1926-01-07 George Wallace Bryant Improvements in or relating to rotary internal combustion engines, pumps and the like
GB334966A (en) * 1929-06-18 1930-09-18 Herbert Charteris Flind Improvements in the construction of motive power engines and pumps
US2495760A (en) * 1946-05-17 1950-01-31 Pinkel Isadore Irving Rotary pump for high-altitude aircraft
FR1290474A (fr) * 1961-04-26 1962-04-13 Rotor Societa Meccanica Italia Mécanisme destiné à déterminer des chambres à volume réglable et variable cycliquement
CH418836A (de) * 1961-12-20 1966-08-15 Consulta Treuhand Gmbh Drehender Energieumwandler und seine Verwendung für einen Antrieb
DE1812773A1 (de) * 1967-12-13 1969-07-03 Aksjeselskabet Pusnes Mek Verk Vorrichtung an hydraulischer Pumpe oder Motor
DE2262131A1 (de) * 1972-12-19 1974-06-20 Eugen Dr Med Ferrari Explosionsrotations-motor
GB1569144A (en) * 1976-10-23 1980-06-11 Inst Cercetare Si Proiectare T Rotary positive displacement fluid machine

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE180927C (fr) *
US805552A (en) * 1904-07-02 1905-11-28 Leopold Vom Hofe Rotary pump.
US1298140A (en) * 1916-10-17 1919-03-25 Lewis E Workman Rotary gas-engine.
US2215096A (en) * 1937-09-02 1940-09-17 Clemons J Z Fanberg Rotary internal combustion motor
US3847123A (en) * 1968-01-22 1974-11-12 R Vierling Rotary fluid power devices
US3940925A (en) * 1974-01-28 1976-03-02 Kelley Arthur P Rotary internal combustion engine

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE225311C (fr) *
DE156261C (fr) *
US1408839A (en) * 1920-11-29 1922-03-07 Sparrow Charles Mck Rotary pump and engine
GB245277A (en) * 1925-01-14 1926-01-07 George Wallace Bryant Improvements in or relating to rotary internal combustion engines, pumps and the like
GB334966A (en) * 1929-06-18 1930-09-18 Herbert Charteris Flind Improvements in the construction of motive power engines and pumps
US2495760A (en) * 1946-05-17 1950-01-31 Pinkel Isadore Irving Rotary pump for high-altitude aircraft
FR1290474A (fr) * 1961-04-26 1962-04-13 Rotor Societa Meccanica Italia Mécanisme destiné à déterminer des chambres à volume réglable et variable cycliquement
CH418836A (de) * 1961-12-20 1966-08-15 Consulta Treuhand Gmbh Drehender Energieumwandler und seine Verwendung für einen Antrieb
DE1812773A1 (de) * 1967-12-13 1969-07-03 Aksjeselskabet Pusnes Mek Verk Vorrichtung an hydraulischer Pumpe oder Motor
DE2262131A1 (de) * 1972-12-19 1974-06-20 Eugen Dr Med Ferrari Explosionsrotations-motor
GB1569144A (en) * 1976-10-23 1980-06-11 Inst Cercetare Si Proiectare T Rotary positive displacement fluid machine

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0137421A2 (fr) * 1983-10-10 1985-04-17 Wankel, Felix, Dr. h.c. Machine à piston rotatif à axe externe
EP0137421A3 (fr) * 1983-10-10 1985-05-15 Wankel, Felix, Dr. H.C.

Also Published As

Publication number Publication date
US4490101A (en) 1984-12-25

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